JP2006207994A - Evaporator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an evaporator with excellent drainability of condensate. <P>SOLUTION: This evaporator 1 is arranged with a space along a longitudinal direction, and is provided with a plurality of heat transfer tubes 12 extended vertically. A drainage promoting member 30 extended vertically is arranged between the longitudinally adjacent heat transfer tubes 12. A gap 70 is provided between the two longitudinally adjacent heat transfer tubes 12, and the drainage promoting member 30 disposed between the both transfer tubes 12, and the gaps 70 serve as drainage channel 60. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an evaporator incorporated in, for example, a car air conditioner that is a refrigeration cycle mounted in an automobile.

  In this specification and claims, the downstream side in the ventilation direction (the side indicated by the arrow X in FIGS. 1 and 10 and the right side in FIG. 4) is referred to as the front, and the opposite side is referred to as the rear. It is assumed to be up and down and left and right.

  Conventionally, as an evaporator for a car air conditioner, a plurality of flat hollow bodies formed by brazing peripheral edges with a pair of plate-shaped plates facing each other are arranged in parallel, and 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. As an evaporator satisfying such requirements, heat exchange tube groups composed of a plurality of flat heat exchange tubes arranged at intervals are arranged in two rows in the ventilation direction, and heat adjacent to the left and right direction. A heat exchange core part formed by arranging corrugated fins between the exchange pipes, and a heat exchange pipe arranged at one end of the heat exchange pipe and connected to the heat exchange pipes of one row of heat exchange pipe groups. 1 header, a second header disposed on the rear side of the first header on one end side of the heat exchange pipe, and connected to a heat exchange pipe of a row of heat exchange pipe groups, and on the other end side of the heat exchange pipe The heat of the heat exchanger tube group which is arrange | positioned and the heat exchanger tube connected to the 1st header is connected, and the heat exchanger tube group which is arrange | positioned at the other end side of the heat exchanger tube, and is connected to the 2nd header. And a fourth header to which an exchange pipe is connected. A refrigerant inlet is formed at the end, a refrigerant outlet is formed at the same end as the refrigerant inlet in the second header, and the inside of the first and second headers is partitioned by a partition plate at an intermediate portion in the length direction. An evaporator is known in which the refrigerant flowing into the first header passes through all the heat exchange tubes and all the headers and flows out from the refrigerant outlet (see Patent Document 1).

By the way, in the evaporator of patent document 1, since the size and weight reduction and performance improvement are achieved compared with the laminated | stacked evaporator mentioned above, the amount of condensed water generated on the surface of a corrugated fin increases. However, according to the evaporator of patent document 1, the drainage property when condensed water increases is not enough.
JP 2003-214794 A

  An object of the present invention is to provide an evaporator that solves the above problems and is excellent in drainage of condensed water.

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

1) An evaporator provided with a plurality of heat exchange tubes arranged at intervals in the front-rear direction and extending in the vertical direction,
An evaporator in which a drainage promotion member extending in the vertical direction is disposed between heat exchange pipes adjacent to each other in the front and rear, and a drainage channel is formed between the front and rear heat exchange pipes and the drainage promotion member.

  2) There is a gap between at least one of the two heat exchange pipes adjacent to the front and back and the drainage promotion member disposed between the two heat exchange pipes, and this gap becomes a drainage channel. The evaporator according to 1) above.

  3) At least one of the two heat exchange pipes adjacent to the front and rear is in contact with the drainage promotion member disposed between the two heat exchange pipes, and the drainage promotion member is in contact with the heat. The above described 1), wherein a recess that is recessed inward in the left-right direction and extending in the up-down direction from the extended surfaces of the left and right side surfaces of the heat exchange tube is formed between the exchange tube and the recess is a drainage channel. Evaporator.

  4) The evaporator according to any one of the above items 1) to 3), wherein the heat exchange tube is flat and is disposed with its width direction directed in the front-rear direction.

  5) The evaporator according to any one of the above 1) to 4), wherein drainage grooves extending in the vertical direction are formed on at least one of the left and right side surfaces of the drainage promotion member.

  6) The above 1) description, wherein the heat exchange pipe is flat and the width direction thereof is arranged in the front-rear direction, and the thickness of the drainage promotion member is equal to the thickness of the heat exchange pipe in the left-right direction. The evaporator.

  7) There is a gap between at least one of the two heat exchange pipes adjacent to the front and rear and the drainage promotion member disposed between the two heat exchange pipes, and this gap serves as a drainage channel. The above 6) satisfying the relation 0 <w / h ≦ 1/4, where h (mm) is the thickness in the left-right direction of the heat exchange pipe and drainage promotion member, and w (mm) is the width in the front-rear direction of the gap. The described evaporator.

8) At least one of the two heat exchange pipes adjacent to the front and rear is in contact with the drainage promotion member disposed between the two heat exchange pipes, and the drainage promotion member is in contact with the heat. A recess that is recessed inward in the left-right direction and extending in the up-down direction from the extended surfaces of the left and right side surfaces of the heat exchange tube is formed between the exchange tube and this recess serves as a drainage channel. Evaporator satisfying the relationship of 0.05 ≦ S / h ≦ 1.5, where S is (mm ² ) and the thickness in the left-right direction of the heat exchange pipe and drainage promotion member is h (mm).

  9) The horizontal cross-sectional shapes of the end wall outer surface on the drainage promotion member side in the front and rear heat exchange pipes and the front and rear surfaces of the drainage promotion member are arc-shaped, respectively, according to any one of 6) to 8) above Evaporator.

  10) Either the outer wall of the end wall on the drainage promotion member side in the front or rear heat exchange pipe or the front and rear faces of the drainage promotion member has a circular cross section, and the other is perpendicular to the left and right side surfaces of the heat exchange pipe The evaporator according to any one of 6) to 8), wherein the evaporator is a flat surface.

  11) The horizontal cross-sectional shape of one of the end wall outer surface on the drainage promotion member side in the front and rear heat exchange pipes and the front and rear surfaces of the drainage promotion member is an arc shape, and the other horizontal cross-sectional shape is a V shape The evaporator according to any one of 6) to 8).

  12) The evaporator according to any one of the above 6) to 8), wherein the horizontal cross-sectional shapes of the end wall outer surface on the drainage promotion member side in the front and rear heat exchange pipes and the front and rear surfaces of the drainage promotion member are respectively V-shaped.

  13) The horizontal cross-sectional shape of one of the end wall outer surface on the drainage promotion member side in the front and rear heat exchange tubes and the front and rear surfaces of the drainage promotion member is V-shaped, and the other is perpendicular to the left and right side surfaces of the heat exchange tube The evaporator according to any one of 6) to 8), wherein the evaporator is a flat surface.

  14) There is a gap between at least one of the two heat exchange pipes adjacent to the front and rear, and the drainage promotion member disposed between the two heat exchange pipes, and this gap serves as a drainage channel. When the thickness of the heat exchange pipe and drainage promotion member in the left-right direction is h (mm) and the width in the front-rear direction of the drainage channel is w (mm), the relationship 0 <w / h ≦ 1/4 is satisfied. The evaporator according to 6) above, wherein the outer surface of the end wall of the heat exchange pipe facing the outer surface and the outer surface of the drainage promotion member facing the drainage channel are flat surfaces perpendicular to the left and right side surfaces of the heat exchange pipe, respectively.

  15) The evaporator according to any one of 6) to 14) above, wherein a drainage groove extending in the vertical direction is formed on at least one of the left and right side surfaces of the drainage promotion member.

  16) A heat exchange core section configured by arranging a plurality of rows of heat exchange pipes arranged at intervals in the front-rear direction, and a heat exchange core section composed of a plurality of heat exchange pipes arranged at intervals in the left-right direction. A first header arranged on one end side of the pipe and connected to heat exchange pipes of at least one row of heat exchange pipe groups; arranged on the rear side of the first header on one end side of the heat exchange pipe; A second header to which a heat exchange pipe of the heat exchange pipe group is connected, a third header that is disposed on the other end side of the heat exchange pipe and connected to the first header, and a heat A fourth header to which the heat exchange pipe of the heat exchange pipe group which is arranged on the other end side of the exchange pipe and connected to the second header is connected, and between the heat exchange pipes adjacent to each other in the front and rear In any one of 1) to 15) above, a drainage promotion member extending in the vertical direction is disposed. Evaporator.

  17) The evaporator according to 16) above, wherein the first header and the second header are integrated.

  18) The first header and the second header form a part on the heat exchange pipe side of both headers, and the first member to which the heat exchange pipe is connected and the part on the opposite side of the heat exchange pipe in both headers The evaporator according to 17) above, further comprising a second member formed and brazed to the first member, whereby both headers are integrated.

  19) The evaporator according to any one of 16) to 18), wherein the third header and the fourth header are integrated.

  20) The third header and the fourth header form a part on the heat exchange pipe side of both headers, and the first member to which the heat exchange pipe is connected, and the part on the opposite side of the heat exchange pipe in both headers The evaporator according to the above item 19), further comprising a second member formed and brazed to the first member, whereby both headers are integrated.

  21) The first header is a refrigerant inlet header having a refrigerant inlet, the second header is a refrigerant outlet header having a refrigerant outlet, and the third header is a refrigerant flowing from the refrigerant inlet header through the heat exchange pipe. The refrigerant inflow header, the fourth header is a refrigerant outflow header through which the refrigerant flows out to the refrigerant outlet header through the heat exchange pipe, and the third header and the fourth header are in communication with each other. The evaporator according to any one of 20).

  22) A refrigeration cycle comprising a compressor, a condenser, and an evaporator, and using a chlorofluorocarbon refrigerant, wherein the evaporator comprises the evaporator according to any one of 1) to 21) above.

  23) A refrigeration cycle comprising a compressor, a gas cooler, an evaporator, a decompressor, and an intermediate heat exchanger for exchanging heat between the refrigerant coming out of the gas cooler and the refrigerant coming out of the evaporator, and using a supercritical refrigerant. A supercritical refrigeration cycle comprising the evaporator according to any one of 1) to 21) above.

  24) A vehicle on which the refrigeration cycle described in 22) or 23) above is mounted as a car air conditioner.

  In the evaporators 1) to 4), a plurality of heat exchange tubes arranged at intervals in the front-rear direction are arranged at intervals in the left-right direction, and between the heat exchange tubes adjacent in the left-right direction. Fins are arranged and joined to the heat exchange tubes. According to this evaporator, the condensed water generated on the surface of the fin is attracted to the joint portion between the heat exchange tube and the fin by the capillary effect, and is condensed to the joint portion between the rear heat exchange tube and the fin. Water flows to the front side by the wind flowing through the ventilation gap between the heat exchange tubes adjacent in the left-right direction, and is drawn to the drainage promotion member side by the capillary effect, and the drainage channel between the heat exchange tube and the drainage promotion member Get inside. And when the space | interval of the heat exchange pipes adjacent before and behind is made the same as the evaporator of patent document 1, the drainage channel cross-sectional area of the drainage channel formed between the front and back heat exchange tubes and the drainage promotion member is Since it becomes comparatively small, the condensed water is drained downward through the drainage channel without being accumulated in the drainage channel due to the capillary effect. Therefore, the drainage of the evaporator is improved. And since the drainage of condensed water improves, it becomes possible to suppress the freezing of condensed water in a drainage channel, and it can prevent the fall of the cooling performance of an evaporator.

  According to the evaporator of 5) above, the condensed water that has flowed to the drainage promotion member side due to the influence of the wind and the capillary effect is drained downward along the drainage groove of the drainage promotion member, improving drainage performance. To do.

  According to the evaporators 7) and 9) to 13), the condensed water that has entered the drainage channel formed by the gap between the heat exchange pipe and the drainage promotion member is efficiently drained downward through the drainage channel. The Therefore, the drainage of condensed water improves.

  According to the evaporators 8) and 9) to 13) above, the condensed water that has entered the drainage channel consisting of a recess formed between the heat exchange pipe and the drainage promotion member passes through the drainage channel efficiently. It is drained downward.

  According to the evaporator of 14), the condensed water that has entered the drainage channel formed by the gap between the heat exchange pipe and the drainage promotion member is efficiently drained downward through the drainage channel. Therefore, the drainage of condensed water improves.

  According to the evaporator of 15) above, the condensed water that has flowed to the drainage promotion member side due to the influence of the wind and the capillary effect is drained downward along the drainage groove of the drainage promotion member, improving drainage performance. To do.

  Embodiments of the present invention will be described below with reference to the drawings.

  In the following description, the term “aluminum” includes aluminum alloys in addition to pure aluminum.

Embodiment 1
This embodiment is shown in FIGS.

  1 and 2 show the overall configuration of the evaporator, and FIGS. 3 to 9 show the configuration of the main part. FIG. 10 shows how the refrigerant flows in the evaporator.

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

  The refrigerant inlet / outlet tank (2) includes a refrigerant inlet header (5) (first header) located on the front side (downstream side in the ventilation direction) and a refrigerant outlet header (6) located on the rear side (upstream side in the ventilation direction) ( 2nd header), and are mutually connected and integrated by connecting means to be described later. An aluminum refrigerant inlet pipe (7) is connected to the refrigerant inlet header (5) of the refrigerant inlet / outlet tank (2), and an aluminum refrigerant outlet pipe (8) is also connected to the refrigerant outlet header (6).

  The refrigerant turn tank (3) includes a refrigerant inflow header (9) (third header) located on the front side and a refrigerant outflow header (11) (fourth header) located on the rear side. (9) and (11) are connected and integrated with each other by the connecting portion (10), and the drainage basin (20) is formed by the headers (9) and (11) and the connecting portion (10) (see FIG. 4). ).

  The heat exchange core section (4) is composed of a plurality of heat exchange pipe groups (13) each including a plurality of heat exchange pipes (12) arranged in parallel at intervals in the left-right direction. Are arranged in two rows, the ventilation gap between adjacent heat exchange tubes (12) of each heat exchange tube group (13), and the heat exchange tubes (12) at the left and right ends of each heat exchange tube group (13). Corrugated fins (14) are respectively arranged on the outer sides and brazed to the heat exchange pipe (12). Between the heat exchange pipes (12) adjacent to the front and rear, an aluminum drainage promotion member (30) extending in the vertical direction is disposed and brazed to the corrugated fin (14). Aluminum side plates (15) are respectively arranged outside the corrugated fins (14) at the left and right ends and brazed to the corrugated fins (14). The upper and lower ends of the heat exchange pipe (12) of the front heat exchange pipe group (13) are connected to the refrigerant inlet header (5) and the refrigerant inflow header (9) to form an outgoing refrigerant circulation section. The upper and lower ends of the heat exchange pipe (12) of the rear heat exchange pipe group (13) are connected to the refrigerant outlet header (6) and the refrigerant outflow header (11) to form a return side refrigerant circulation section.

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

  The first member (16) has curved portions (22) having a small cross-sectional arc shape with a central portion projecting downward at both front and rear side portions thereof. A plurality of tube insertion holes (23) that are long in the front-rear direction are formed in each bending portion (22) at intervals in the left-right direction. The tube insertion holes (23) of the front and rear curved portions (22) are at the same position in the left-right direction. Standing walls (22a) are integrally formed over the entire length at the front edge of the front curved portion (22) and the rear edge of the rear curved portion (22), respectively. Further, a flat portion (24) constituting a means for connecting the refrigerant inlet header (5) and the refrigerant outlet header (6) is formed between both curved portions (22) of the first member (16), and the flat portion In (24), a plurality of through holes (25) are formed at intervals in the left-right direction.

  The second member (17) has a substantially m-shaped cross section that opens downward, and is provided in the center between the front and rear walls (26) extending in the left-right direction and the front and rear walls (26) and extends in the left-right direction. In addition, a partition wall (27) as a partition means for partitioning the refrigerant inlet / outlet tank (2) into two front and rear spaces, and an upper portion connecting the front and rear walls (26) and the upper ends of the partition wall (27) together. And two substantially arc-shaped connecting walls (28) projecting from each other. The partition wall (27) constitutes means for connecting the refrigerant inlet header (5) and the refrigerant outlet header (6). The lower end portion of the rear wall (26) of the second member (17) and the lower end portion of the partition wall (27) are partition means for partitioning the refrigerant outlet header (6) into two upper and lower spaces (6a) and (6b). Are integrally connected over the entire length by a shunt resistor plate (29). A plurality of refrigerant passage holes (31A) (31B) that are long in the left-right direction are formed in a penetrating manner at intervals in the left-right direction in the portion excluding the left and right end portions in the rear portion of the shunt resistor plate (29). ing. The lower end of the partition wall (27) protrudes downward from the lower ends of the front and rear walls (26), and a plurality of lower walls protrude downward and are fitted into the through holes (25) of the first member (16). The protrusions (27a) are integrally formed with an interval in the left-right direction. The protrusion (27a) is formed by cutting a predetermined portion of the partition wall (27).

  On the front side of the right cap (19), a left protruding portion (32) that is fitted into the refrigerant inlet header (5) is integrally formed, and on the rear side, a resistance for shunting the refrigerant outlet header (6) is formed. Upper left protrusion (33) that fits in the space (6a) above the plate (29), and lower side that fits in the space (6b) below the shunt resistor plate (29) The left projecting portion (34) is integrally formed with a space in the vertical direction. The arcuate portion between the front and rear side edges and the upper edge of the right cap (19) is integrally formed with an engaging claw (35) projecting to the left, and the front portion and the rear side of the lower edge are also formed. Engaging claws (36) projecting to the left are formed integrally with the part. A refrigerant inlet (37) is formed in the bottom wall of the front left protrusion (32) of the right cap (19), and a refrigerant outlet (38) is also formed in the bottom wall of the rear upper left protrusion (33). Is formed. The left cap (18) is symmetrical with the right cap (19) and has a right protrusion (39) fitted into the refrigerant inlet header (5) and a shunt resistor plate (29) of the refrigerant outlet header (6). ) Upper right protrusion (41) fitted into the upper space (6a), lower right protrusion fitted into the lower space (6b) than the shunt resistor plate (29) (42) and upper and lower engaging claws (43) and (44) protruding rightward are integrally formed. No opening is formed in the bottom wall of the right protrusion (39) and the upper right protrusion (41). The upper edges of the caps (18) and (19) have two substantially arcuate portions at the center in the front-rear direction so that they coincide with both ends of the upper surface of the second member (17) of the refrigerant inlet / outlet tank (2). It is shaped like a single piece. Further, the lower edges of the caps (18) and (19) have such a shape that two substantially arc-shaped portions having a small curvature are integrally connected via a flat portion at the center in the front-rear direction.

  And the front curved part (22) and flat part (24) of the first member (16), the front wall (26), the partition wall (27) and the front connection wall (28) of the second member (17), The refrigerant inlet header (5) is formed by the front portions of the left and right caps (18) and (19), the rear curved portion (22) and the flat portion (24) of the first member (16), and the second member. (17) The refrigerant outlet header (6) is formed by the rear wall (26), the partition wall (27), the rear connection wall (28), and the rear portions of the left and right caps (18) (19). ing. The refrigerant inlet header (5) and the refrigerant outlet header (6) are connected and integrated by a flat portion (24) and a partition wall (27).

  The joint plate (21) has a short cylindrical refrigerant inlet (45) leading to the refrigerant inlet (37) of the right cap (19) and a short cylindrical refrigerant outlet (46) also leading to the refrigerant outlet (38). I have. Bent portions (47) protruding leftward are formed at portions between the refrigerant inlet (45) and the refrigerant outlet (46) at both upper and lower edges of the joint plate (21). The upper bent portion (47) is engaged between the two substantially arc-shaped portions at the upper edge of the right cap (19) and between the two connecting walls (28) of the second member (17). The lower bent portion (47) is engaged with the flat portion formed between two substantially arc-shaped portions at the lower edge of the right cap (19) and the flat portion (24) of the first member (16). Match. Furthermore, engaging claws (48) protruding leftward are integrally formed at both front and rear end portions of the lower edge of the joint plate (21). The engaging claw (48) is engaged with the lower edge of the right cap (19). A reduced diameter portion formed at one end of the refrigerant inlet pipe (7) is inserted into the refrigerant inlet (45) of the joint plate (21) and brazed, and similarly to the refrigerant outlet (46), the refrigerant outlet pipe A reduced diameter portion formed at one end of (8) is inserted and brazed. Although not shown, an expansion valve mounting member is joined to the other ends of the refrigerant inlet pipe (7) and the refrigerant outlet pipe (8) so as to straddle both pipes (7) and (8).

  The first and second members (16), (17), the caps (18), (19), and the joint plate (21) of the refrigerant inlet / outlet tank (2) are brazed as follows. That is, the first and second members (16), (17) are inserted into the through holes (25) of the first member (16) by the protrusions (27a) of the second member (17) and caulked. The brazing of the first member (16) with the upper ends of the front and rear rising walls (22a) of the one member (16) engaged with the lower ends of the front and rear walls (26) of the second member (17) They are brazed together using a layer of material. Both caps (18) and (19) are arranged so that the front protrusions (39) and (32) are in the space on the front side of the partition walls (27) in both members (16) and (17), and the rear upper protrusions ( 41) (33) is located behind the partition wall (27) in both members (16) and (17) and above the shunt resistor plate (29), and the rear lower protrusion (42 ) (34) are respectively fitted in the spaces behind the partition wall (17) and below the shunt resistor plate (29), and the upper engaging claws (43) (35) are second With the lower engaging claws (44) (36) engaged with the curved portion (22) of the first member (16) engaged with the connecting wall (28) of the member (17), The first and second members (17) and (17) are brazed using the brazing material layers of both caps (18) and (19). In the joint plate (21), the bent portion (47) is engaged with the right cap (19) and the second member (17), and the engaging claw (48) is engaged with the right cap (19). Thus, the right cap (19) is brazed using the brazing material layer of the right cap (19).

  Thus, the refrigerant inlet / outlet tank (2) is formed, and the refrigerant outlet header (6) is partitioned into upper and lower spaces (6a) (6b) by the shunt resistor plate (29), and these spaces (6a) ( 6b) communicates with the refrigerant passage holes (31A) and (31B). The refrigerant outlet (38) of the right cap (19) communicates with the upper space (6a) of the refrigerant outlet header (6).

  As shown in FIGS. 4-6, the refrigerant | coolant turn tank (3) is formed from the aluminum brazing sheet | seat which has a brazing material layer on both surfaces, and the plate-shaped 1st to which all the heat exchange pipe | tubes (12) were connected. Formed from an aluminum brazing sheet comprising a member (50), a second member (51) made of a bare material formed from an extruded aluminum material and covering the lower side of the first member (50), and a brazing material layer on both sides Aluminum caps (52) (53) that are closed at both ends, drainage auxiliary plates (54) made of aluminum bare material that are long in the left-right direction joined to the connecting portion (10), and the outer surface of the right cap (52) And a communication member (55) made of an aluminum bare material that is brazed so as to straddle the refrigerant inflow header (9) and the refrigerant outflow header (11), and the refrigerant passes through the communication member (55). Inflow header (9) and refrigerant outflow header (11) are at the right end It is made to communicate with.

  The refrigerant inflow header (9) and the refrigerant outflow header (11) each have a top surface, front and rear side surfaces, and a bottom surface. The top surfaces of both headers (9) and (11) are horizontal flat surfaces (9a) and (11a) except for the inner and outer portions in the front-rear direction. A first low-order part (9b) (11b) is formed of an inclined surface linearly inclined downward. And the 1st low-order part (9b) (11b) is the front-and-rear both sides | surfaces of a drainage basin (20), and the front-and-rear both sides | surfaces of a drainage basin (20) are spread outward in the front-back direction. It is preferable that the downward inclination angle with respect to the horizontal plane of the first low-order parts (9b) and (11b) is 45 degrees or more. The front and rear sides of the drainage basin (20), that is, the first low-order parts (9b) and (11b) of the headers (9) and (11) are straight if they extend outward in the front-rear direction. It may be curved, not limited to the one that is inclined. In addition, the front and rear direction outer portions of the top surfaces of both headers (9) and (11) have a second lower portion (9c) comprising an inclined surface linearly inclined downward toward the outer side in the front and rear direction with respect to the horizontal plane. (11c) is formed. It is preferable that the downward inclination angle with respect to the horizontal plane of the second low-order parts (9c) and (11c) is 45 degrees or more. The front and rear outer surfaces of both headers (9) and (11) are connected to the second low-order parts (9c) and (11c) of the top surface.

  The first member (50) includes a first header forming part (56) that forms the upper part of the refrigerant inflow header (9), a second header forming part (57) that forms the upper part of the refrigerant outflow header (11), The header forming portions (56) and (57) are connected to each other and the connecting wall (58) is formed to form the connecting portion (10). The first header forming portion (56) is formed of a horizontal flat top wall (56a) and a first inclined wall integrally formed over the entire length of the rear edge of the top wall (56a) and inclined downward toward the rear. 56b), a second inclined wall (56c) formed integrally with the front edge of the top wall (56a) over the entire length and inclined downward toward the front, and a front edge of the second inclined wall (56c) It consists of a hanging wall (56d) integrally formed over the entire length. The second header forming portion (57) includes a horizontal flat top wall (57a) and a first inclined wall (integrally formed over the entire length of the front edge of the top wall (57a) and inclined downward toward the front ( 57b), a second inclined wall (57c) formed integrally with the rear edge of the top wall (57a) and inclined downward toward the rear, and a rear edge of the second inclined wall (57c) A hanging wall (57d) integrally formed over the entire length. The lower edge of the first inclined wall (56b) of the first header forming portion (56) and the lower edge of the first inclined wall (57b) of the second header forming portion (57) are integrated by the connecting wall (58). It is connected to. The lower end surfaces of the hanging walls (56d) and (57d) of the header forming portions (56) and (57) are inclined downward inward in the front-rear direction, and a step portion (69 described later) is formed by an outer portion of the lower end surfaces. ) Is formed. The upper surface of the top wall (56a) of the first header forming portion (56) forms the horizontal flat surface (9a) of the top surface of the refrigerant inflow header (9), and the outer surfaces of both inclined walls (56b) (56c) are both. The lower portions (9b) and (9c) are formed, and the outer surface of the hanging wall (56c) forms the upper portion of the front side surface. The top surface of the top wall (57a) of the second header forming portion (57) forms a horizontal flat surface (11a) of the top surface of the refrigerant outflow header (11), and the outer surfaces of both inclined walls (57b) (57c) are both. The lower portion (11b) (11c) is formed, and the outer surface of the hanging wall (57d) forms the upper portion of the rear side surface.

  A plurality of tube insertion holes (59) that are long in the front-rear direction are formed in both header forming portions (56), (57) of the first member (50) at intervals in the left-right direction. The pipe insertion holes (59) of both header forming portions (56) (57) are at the same position in the left-right direction. The connecting portion (10) side end portion of the tube insertion hole (59), that is, the rear end portion of the tube insertion hole (59) of the first header forming portion (56) and the tube insertion hole of the second header forming portion (57) ( 59) are located on the first inclined walls (56b) and (57b), respectively, so that the end of the pipe insertion hole (59) on the connecting part (10) side is located on the side surface of the drainage basin (20). positioned. In addition, the outer end in the front-rear direction of the pipe insertion hole (59), that is, the front end of the pipe insertion hole (59) of the first header forming part (56) and the pipe insertion hole (59) of the second header forming part (57) The rear ends are located on the second inclined walls (56c) and (57c), respectively, so that the outer ends in the front-rear direction of the pipe insertion holes (59) are located on the top surfaces of both headers (9) and (11). It is located in the second lower part (9c) (11c).

  The pipe insertion holes (59) of the top walls (56a) (57a) and the inclined walls (56b) (56c) (57b) (57c) of both header forming portions (56) (57) of the first member (50) The left and right side portions are inclined portions (61) inclined downward toward the tube insertion holes (59), and the recesses (62) are formed by the inclined portions (61) on the left and right sides of each tube insertion hole (59). Is formed. On the outer surfaces of the second inclined walls (56c) (57c) and the hanging walls (56d) (57d) of both header forming portions (56) (57) of the first member (50), condensed water is supplied to the refrigerant turn tank ( 3) A drainage groove (63) for draining downward is formed continuously to the outer end in the front-rear direction of the pipe insertion hole (59). The bottom of the drainage groove (63) gradually goes downward as it goes away from the pipe insertion hole (59). The second inclined wall (56c) (57c) in the drainage groove (63), that is, the groove bottom of the portion existing in the second low-order part (9c) (11c), is downward toward the outside in the front-rear direction with respect to the horizontal plane. It is inclined linearly. It is preferable that the downward inclination angle with respect to the horizontal surface of the groove bottom of the portion of the drainage groove (63) existing in the second low-order part (9c) (11c) is 45 degrees or more. The lower ends of the portions of the drainage grooves (63) existing on the hanging walls (56d) and (57d) are opened at the lower end surfaces of the hanging walls (56d) and (57d).

  In the connecting wall (58) of the first member (50), a plurality of drainage through holes (64) elongated in the left-right direction are formed at intervals in the left-right direction. In addition, a plurality of fixing through holes (65) are formed in the connecting wall (58) of the first member (50) at intervals in the left-right direction so as to be shifted from the drain through holes (64). Has been.

  The second member (51) includes a first header forming part (66) that forms the lower part of the refrigerant inflow header (9), a second header forming part (67) that forms the lower part of the refrigerant outflow header (11), The header forming portions 66 and 67 are connected to each other and are connected to the connecting wall 58 of the first member 50 to be connected to the connecting wall 68 to form the connecting portion 10. The first header forming portion (66) includes a vertical front and rear walls (66a), a bottom wall (66b) having a substantially arcuate cross section projecting downward and integrally connecting lower ends of the front and rear walls (66a). It becomes more. The second header forming portion (67) includes a vertical front and rear walls (67a) and a bottom wall (67b) having a substantially arcuate cross section projecting downward to integrally connect lower ends of the front and rear walls (67a). And a horizontal diversion control wall (67c) for integrally connecting the upper ends of the front and rear walls (67a). The upper end portion of the rear wall (66a) of the first header forming portion (66) and the upper end portion of the front wall (67a) of the second header forming portion (67) are integrally connected by a connecting wall (68). The outer surface of the front wall (66a) of the first header forming part (66) and the outer surface of the rear wall (67a) of the second header forming part (67) are respectively formed on the first header forming part (56) of the first member (50). The outer surface of the hanging wall (56d) and the hanging wall (57d) outer surface of the second header forming portion (57) are located on the inner side in the front-rear direction, whereby the hanging wall (56d) (57d) of the first member (50) And the front and rear walls (66a) and (67a) of the second member (51) are provided with a stepped portion (69), and the outer surfaces of the hanging walls (56d) and (57d) through the stepped portion (69) It is located on the outside in the front-rear direction with respect to the outer surfaces of the wall (66a) and the rear wall (67a), and the entire lower end of the drainage groove (63) opens into the step portion (69) (see FIG. 4). The outer surface of the upper edge of the front wall (66a) of the first header forming portion (66) and the outer surface of the upper edge of the rear wall (67a) of the second header forming portion (67) are suspended in the drainage groove (63). It is flush with the bottom surface of the portion existing on the walls (56d) and (57d). The outer surface of the front wall (66a) of the first header forming portion (66) forms the lower portion of the front side surface of the refrigerant inflow header (9), and the outer surface of the rear wall (67a) of the second header forming portion (67). Forms the lower part of the rear side of the refrigerant outflow header (11).

  A plurality of circular coolant passage holes (71) are formed in the left-right direction at the rear side of the center part in the front-rear direction of the flow dividing control wall (67c) of the second header forming portion (67) of the second member (51). It is formed in a penetrating manner with an interval. The interval between adjacent circular refrigerant passage holes (71) gradually increases as the distance from the left end portion increases. The intervals between adjacent circular coolant passage holes (71) may all be equal. In the connecting wall (68) of the second member (51), drainage through holes (72) that are long in the left-right direction are formed at positions corresponding to the drainage through holes (64) of the first member (50). A fixing through hole (73) is formed at a position corresponding to the fixing through hole (65) of one member (50).

  A notch (74) is formed from the upper edge of the drainage auxiliary plate (54) at the portion corresponding to the drainage through holes (64) and (72) of the first and second members (50) and (51). . The width in the left-right direction of the opening of the notch (74) is equal to the length in the left-right direction of the drainage through holes (64) (72). A drainage auxiliary groove (75) extending in the vertical direction on both front and rear surfaces of the drainage auxiliary plate (54) so as to be connected to the lower end of the notch (74) and having a lower end opened to the lower end surface of the drainage auxiliary plate (54) Is formed. Further, at the upper edge of the drainage auxiliary plate (54), the first and second members (50), (51) are protruded upward at positions matching the fixing through holes (65), (73), and both fixing through holes are provided. (65) A projection (76) is formed which is inserted through (73).

  Each cap (52) (53) has a plate shape and is formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides. On the front side of the right cap (52), a left projecting portion (77) fitted into the refrigerant inflow header (9) is integrally formed, and on the rear side, the flow dividing control wall of the refrigerant outflow header (11) is formed. (67c) Upper left protrusion (78) fitted into the space (11A) above and (67c) lower left side fitted into the space (11B) below the flow dividing control wall (67c) The protruding portion (79) is integrally formed with a vertical interval. In addition, an engagement claw (81) protruding leftward is formed on the arc-shaped portion between the front and rear side edges and the lower edge of the right cap (52) and the portion near the front and rear ends of the upper edge. Engaging claws (82) projecting to the right are formed at the center in the front-rear direction of both edges. Through holes (83) and (84) are formed in the bottom wall of the front left protrusion (77) on the front side of the right cap (52) and the bottom wall of the lower left protrusion (79) on the rear side, respectively. . The front through hole (83) communicates the inside of the refrigerant inflow header (9) to the outside, and the rear through hole (84) is a space below the flow dividing control wall (67c) of the refrigerant outflow header (11) ( 11B) Let the inside communicate with the outside.

  On the front side of the left cap (53), a right protruding portion (85) fitted into the refrigerant inflow header (9) is integrally formed, and on the rear side, the flow dividing control wall of the refrigerant outflow header (11) is formed. Upper right protrusion (86) that fits in space (11A) above (67c), and lower right that fits in space (11B) below shunt control wall (67c) The projecting portion (87) is integrally formed with a vertical spacing. In addition, an engaging claw (88) projecting to the right is formed integrally with the arc-shaped portion between the front and rear side edges and the lower edge of the left cap (53) and the upper edge near the front and rear ends. Yes. No through hole is formed in the bottom wall of the right protrusion (85) and the lower right protrusion (87).

  The communicating member (55) is formed by pressing an aluminum bare material, and has a plate shape that is the same shape and size as the right cap (52) when viewed from the right. The outer surface of the cap (52) is brazed. The communication member (55) is formed with an outward bulging portion (89) so as to be passed through the two through holes (83) and (84) of the right cap (52). The inside of the outward bulging portion (89) serves as a communication path (91) that allows both through holes (83) and (84) of the right cap (52) to pass therethrough. Further, a notch (92) into which the engaging claw (82) of the right cap (52) is fitted is formed in the center part in the front-rear direction on both upper and lower edges of the communication member (55).

  The first and second members (50) and (51) of the refrigerant turn tank (3), the drainage auxiliary plate (54), the caps (52) and (53), and the communication member (55) are as follows. It is brazed. That is, the first member (50) and the second member (51) have a connecting through hole (64) (72) between the connecting walls (58) and (68) and a fixing through hole (65) (73). The two header forming portions (56) and (57) have a suspended wall (56d) (57d) lower end, the front wall (66a) of the first header forming portion (66) and the second header forming portion ( 67) The upper end of the rear wall (67a) is engaged, and the protrusion (76) of the drainage auxiliary plate (54) is inserted into the fixing through holes (65) (73) of both members (50) (51). The two members (56) and (57) are temporarily fastened by being caulked, and are brazed to each other using the brazing material layer of the first member (50). The drainage auxiliary plate (54) is brazed to the connecting walls (58) and (68) of both members (50) and (51) using the brazing material layer of the first member (50). Both caps (52) and (53) have rear protrusions (77) and (85) in the space formed by the first header forming portions (56) and (66) of both members (50) and (51). On the upper side of the flow dividing control wall (67c) in the space formed by the second header forming portions (57) and (67) of the two members (50) and (51). In addition, the rear lower protrusions (79) and (87) are lower than the flow dividing control wall (67c) in the space formed by the second header forming portions (57) and (67) of both members (50) and (51). The upper engaging claws (81) and (88) are engaged with the first member (50), and the lower engaging claws (81) and (88) are engaged with the second member. In the state of being engaged with (51), the first and second members (50) (51) are brazed using the brazing material layer of each cap (52) (53). The communicating member (55) is engaged with the communicating member (55) so that the engaging claw (82) of the right cap (52) is fitted into the notch (92). The right cap (52) is brazed using a brazing material layer.

  Thus, the refrigerant turn tank (3) is formed, and the refrigerant inflow header (9) is formed by the first header forming portions (56) and (66) of both members (50) and (51), and the second header is also formed. A refrigerant outflow header (11) is formed by the forming portions (57) and (67). The refrigerant outflow header (11) is divided into two upper and lower spaces (11A) and (11B) by a flow dividing control wall (67c), and these spaces (11A) and (11B) are communicated by a circular refrigerant passage hole (71). It has been. The rear through hole (84) of the right cap (52) communicates with the lower space (11B) of the refrigerant outflow header (11). The refrigerant inflow header (9) and the lower space (11B) of the refrigerant outflow header (11) are expanded outwardly of the through holes (83) and (84) of the right cap (52) and the communication member (55). It is connected via the communication path (91) in the exit part (89). Further, a connecting portion (10) is formed by the connecting walls (58) and (68) of both members (50) and (51), and the first low-order portion (9b) of the refrigerant inflow header (9) and the refrigerant outflow header (11 The drainage basin (20) is formed by the first low-order part (11b) and the connecting part (10).

  The heat exchange pipe (12) is made of a bare material formed of an aluminum extruded profile, and has a wide and flat shape in the front-rear direction, and a plurality of refrigerant passages (12a) extending in the length direction are formed in parallel inside the heat exchange pipe (12). ing. The horizontal cross-sectional shape of the outer surfaces of the front and rear end walls of the heat exchange pipe (12) is an arc shape with the center portion protruding outward (see FIG. 8). In the following description, the term “arc-shaped” is not limited to a part of a circle in a strict sense, and includes, for example, a part of an ellipse. The front heat exchange pipe (12) and the rear heat exchange pipe (12) are arranged at the same position in the left-right direction, and the upper end portion of the heat exchange pipe (12) is a refrigerant inlet / outlet tank ( 2) The first member (16) is inserted into the tube insertion hole (23) and brazed to the first member (16) using the brazing material layer of the first member (16). The turn tank (3) is inserted into the tube insertion hole (59) of the first member (50) and brazed to the first member (50) using the brazing material layer of the first member (50). . The front heat exchange pipe (12) communicates with the refrigerant inlet header (5) and the refrigerant inflow header (9), and the rear heat exchange pipe (12) communicates with the refrigerant outlet header (6) and the refrigerant outflow header (11). ).

  Here, the tube height (h) which is the thickness in the left-right direction of the heat exchange tube (12) is 0.75 to 1.5 mm (see FIG. 7), the tube width which is the width in the front-rear direction is 12 to 18 mm, and the peripheral wall The wall thickness of the partition wall is 0.175 to 0.275 mm, the thickness of the partition wall partitioning the refrigerant passages (12a) is 0.175 to 0.275 mm, the pitch of the partition wall is 0.5 to 3.0 mm, both front and rear walls The curvature radius of the outer surface is preferably 0.35 to 0.75 mm.

  As the heat exchange pipe (12), instead of one made of an aluminum extruded shape, a pipe in which a plurality of refrigerant passages are formed by inserting inner fins into an aluminum electric sewing pipe may be used. . Also, two flat wall forming parts formed by rolling an aluminum brazing sheet having a brazing filler metal layer on both sides and connected via connecting parts, and the opposite side of the connecting part in each flat wall forming part A side wall forming portion integrally formed in a protruding shape from the side edges of the flat wall forming portion, and a plurality of partition wall forming portions integrally formed in a protruding shape from the two flat wall forming portions at a predetermined interval in the width direction of the flat wall forming portion. It is also possible to use a plate having a partition wall formed by bending a plate with a hairpin shape at the connecting portion, butting the side wall forming portions with each other and brazing each other.

  The corrugated fin (14) is formed in a corrugated shape using an aluminum brazing sheet having a brazing filler metal layer on both sides, the wave crest (14a), the wave bottom (14b) and the wave crest (14a) and the wave bottom (14b). ) Are connected to each other (see FIG. 7), and a plurality of louvers are formed side by side in the front-rear direction. The corrugated fin (14) is shared by the front and rear heat exchange pipes (12), and the width in the front and rear direction is the front edge of the front heat exchange pipe (12) and the rear edge of the rear heat exchange pipe (12). The interval between and is almost equal. The wave crest (14a) and the wave bottom (14b) of the corrugated fin (14) are brazed to the front and rear heat exchange tubes (12).

  Here, the fin height (H) of the corrugated fin (14) is a linear distance between the wave crest (14a) and the wave bottom (14b), and the fin height (H) is 7.0 mm to 10.0 mm. It is preferable. Further, the fin pitch (Pf) of the corrugated fin (14) is 1/2 of the interval (P) between the vertical center portions of the adjacent wave crest (14a) and wave bottom (14b), that is, (Pf) = P / 2, and the fin pitch (Pf) is preferably 1.3 to 1.8 mm. The corrugated fin (14) has a wave crest (14a) and a wave bottom (14b) that are flatly brazed to the heat exchange pipe (12) in a surface contact manner, and provided on both sides of the flat part and connected to each other. The radius of curvature (R) of the rounded portion is preferably 0.7 mm or less (see FIG. 7).

  As shown in FIGS. 8 and 9, the drainage promotion member (30) is hollow and has a flat shape that is slightly wider in the front-rear direction. The thickness in the left-right direction is the tube of the heat exchange pipe (12). It is equal to the thickness in the left-right direction, which is the height (h). The horizontal cross-sectional shape of both front and rear surfaces of the drainage promotion member (30) is an arc shape with the center portion protruding outward in the front-rear direction. A gap (70) exists between the front and rear side edges of the drainage promotion member (30) and the front and rear heat exchange pipes (12), thereby forming a drainage channel (60). Here, the thickness in the left-right direction of the heat exchange pipe (12) and the drainage promotion member (30) is h (mm), and the width in the front-rear direction of the narrowest part of the gap (70), that is, between the center parts in the left-right direction. When the width of is w (mm), it is preferable that the relationship of 0 <w / h ≦ 1/4 is satisfied. When w / h> ¼, the effect of drawing condensed water to the drainage channel (60) by the capillary effect and the effect of draining the condensed water downward through the drainage channel (60) by the capillary effect are not sufficient There is.

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

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

  In the above-described evaporator (1), as shown in FIG. 10, 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 (7) to the refrigerant inlet of the joint plate (21). Enters the refrigerant inlet header (5) of the refrigerant inlet / outlet tank (2) through the refrigerant inlet (37) of the right cap (19) and the right cap (19). It flows into the refrigerant passage (12a).

  The refrigerant that has flowed into the refrigerant passages (12a) of all the heat exchange tubes (12) flows downward in the refrigerant passages (12a) and enters the refrigerant inflow header (9) of the refrigerant turn tank (3). The refrigerant that has entered the refrigerant inflow header (9) flows to the right, the front through hole (83) of the right cap (52), and the communication path (91 in the outward bulge portion (89) of the communication member (55). ) And the rear through-hole (84) of the right cap (52), it turns to change the flow direction and enters the lower space (11B) of the refrigerant outflow header (11).

  Then, due to the fact that the refrigerant flow from the refrigerant inlet header (5) to the front heat exchange pipe (12) is not sufficiently uniform, the temperature of the refrigerant flowing through the front heat exchange pipe (12) ( Even if there is a bias in the distribution of the refrigerant dryness, the refrigerant is mixed when it turns into the lower space (11B) of the refrigerant outflow header (11) and flows into the lower space (11B) of the refrigerant outflow header (11). The temperature becomes uniform throughout.

  The refrigerant that has entered the lower space (11B) of the refrigerant outflow header (11) flows to the left, enters the upper space (11A) through the circular refrigerant passage hole (71) of the flow dividing control wall (67c), and is divided. And flows into the refrigerant passages (12a) of all the heat exchange tubes (12) on the rear side.

  The refrigerant flowing into the refrigerant passage (12) of the heat exchange pipe (12) changes the flow direction and flows upward in the refrigerant passage (12a) to enter the lower space (6b) of the refrigerant outlet header (6). Then, it enters the upper space (6a) through the oblong coolant passage holes (31A) and (31B) of the shunt resistor plate (29). Here, resistance is imparted to the refrigerant flow by the shunt resistor plate (29), so that the shunt flow from the upper space (11A) of the refrigerant outflow header (11) to the rear heat exchange pipe (12) is made uniform. In addition, the flow from the refrigerant inlet header (5) to the front heat exchange pipe (12) is further uniformized. As a result, the refrigerant circulation amount of all the heat exchange tubes (12) is made uniform, and the temperature distribution of the entire heat exchange core part (4) is made uniform.

  Next, the refrigerant that has entered the upper space (6a) of the refrigerant outlet header (6) passes through the refrigerant outlet (38) of the right cap (19) and the refrigerant outlet (46) of the joint plate (21), and then the refrigerant outlet. It flows out into the pipe (8). While the refrigerant flows through the refrigerant passage (12a) of the front heat exchange pipe (12) and the refrigerant passage (12a) of the rear heat exchange pipe (12), the ventilation gaps are indicated by arrows in FIGS. It exchanges heat with the air flowing in the direction indicated by X and flows out as a gas phase.

  At this time, a large amount of condensed water is generated on the surfaces of the heat exchange pipe (12) and the corrugated fin (14), particularly on the surface of the corrugated fin (14). Most of the generated condensed water flows to the junction side between the wave exchange part (14a) and the wave bottom part (14b) of the heat exchange pipe (12) and the corrugated fin (14) by the capillary effect. The condensed water drawn to the joint between the rear heat exchange pipe (12) and the corrugated fin (14) is moved forward by the wind flowing through the ventilation gap between the heat exchange pipes (12) adjacent in the left-right direction. As it flows, it is drawn toward the drainage promotion member (30) by the capillary effect and enters the drainage channel (60). Then, it is drained downward through the drainage channel (60) by the capillary effect. Accordingly, drainage is improved, and as a result, it is possible to suppress freezing of condensed water, and it is possible to prevent a decrease in the cooling performance of the evaporator. The condensed water drawn to the joint between the front heat exchange pipe (12) and the corrugated fin (14) is moved forward by the wind flowing through the ventilation gap between the heat exchange pipes (12) adjacent in the left-right direction. And is drained downward along the front end face of the front heat exchange pipe (12).

  The condensed water drained downward through the drainage channel (60) enters the drainage basin (20) of the refrigerant turn tank (3), and when the condensed water accumulates in the drainage basin (20) to some extent, It flows out through the through holes (64) and (72) to the lower part of the connecting part (10), flows along the peripheral edge of the notch (74) of the drainage auxiliary plate (54), and enters the drainage auxiliary groove (75). Enters, flows downward in the drainage auxiliary groove (75), and falls from the lower end opening to the lower side of the refrigerant turn tank (3). Condensed water drained downward along the front end face of the front heat exchange pipe (12) enters the drainage groove (63) and flows through the drainage groove (63), that is, its lower end opening, that is, the step part (69). Falls from the opening to the bottom of the refrigerant turn tank (3). Thus, the generated condensed water is drained.

  Hereinafter, experimental examples performed to evaluate the drainage of the evaporator will be described.

Experimental example 1
A test in which the heat exchange pipe (12), the drainage promotion member (30), and the corrugated fin (14) have the configuration of the above embodiment, and the refrigerant inlet / outlet tank (2) and the refrigerant turn tank (3) are not attached. Prepared the body. The thickness h in the left-right direction of the heat exchange pipe (12) and the drainage promotion member (30) is 1.4 mm, and the width w in the front-rear direction of the gap (70) between the heat exchange pipe (12) and the drainage promotion member (30) is The width in the front-rear direction of the drainage promotion member (30) is 3.5 mm, the fin height (H) of the corrugated fin (14) is 8 mm, and the fin pitch (P) is 1.5 mm. Then, both end openings of the heat exchange pipe (12) and the drainage promotion member (30) were sealed. Next, the test specimen was immersed in water in a water tank, and air remaining between the heat exchange tubes (12) and between the corrugated fins (14) was removed and left for 30 minutes. Next, the test specimen was lifted in a vertical state and taken out of the water, and the weight of the test specimen was measured in this state for 1800 seconds to evaluate drainage.

Comparative Experiment Example 1
Except that the drainage promotion member is not arranged between the front and rear heat exchange pipes (12), prepare a test body having the same configuration as in Experimental Example 1, and in the same manner as in Experimental Example 1, evaluated.

  The results of Experimental Example 1 and Comparative Experimental Example 1 are shown in FIG. In addition, in FIG. 11, water retention weight represents the ratio when the evaporator is lifted in a vertical state and taken immediately after being taken out of water to 100%. The fact that the water retention weight is reduced means that the amount of drained water is increased, and the drainage performance is improved.

Embodiment 2
This embodiment is shown in FIG.

In the case of Embodiment 2, the outer surface of the end wall on the inner side in the front-rear direction of both the front and rear heat exchange tubes (12) and the front and rear surfaces of the drainage promotion member (30) are in contact. And, between the front and rear heat exchange pipe (12) and the drainage promotion member (30), a recess (indented inward in the left-right direction and extended in the vertical direction from the extended surfaces of the left and right side surfaces of the heat exchange pipe (12) ( 90) is formed, and this recess (90) is a drainage channel (80). Here, the cross-sectional area of the drainage channel (80) (the portion hatched in FIG. 12) is S (mm ² ), and the thickness of the heat exchange pipe (12) and the drainage promotion member (30) in the horizontal direction is h ( mm), it is preferable that the relationship of 0.05 ≦ S / h ≦ 1.5 is satisfied. When S / h is outside the above range, the effect of attracting condensed water to the drainage channel (80) by the capillary effect and the effect of draining the condensed water downward through the drainage channel (80) by the capillary effect are not sufficient. There is.

  Other configurations are the same as those of the first embodiment.

In the above-described two embodiments, the evaporator according to the present invention is applied to an evaporator of a car air conditioner that uses a chlorofluorocarbon refrigerant, but is not limited thereto, and includes a compressor, a gas cooler, an intermediate heat exchanger, In a vehicle having a car air conditioner having an expansion valve and an evaporator and 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.

  Hereinafter, modifications of the heat exchange pipe and the drainage promotion member will be described.

  As in the case of the first embodiment, FIG. 13 shows a modification in the case where a gap (70) exists between the heat exchange pipe and the drainage promotion member, and this gap (70) is a drainage channel (60). It is an example. In the description of this modification, the same components as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  In the modification shown in FIG. 13 (a), the front and rear surfaces of the drainage promotion member (30A) are flat surfaces that are perpendicular to the left and right surfaces of the heat exchange tube (12).

  In the modification shown in FIG. 13 (b), the outer surface of the rear end wall of the front heat exchange pipe (12A) and the outer surface of the front end wall of the rear heat exchange pipe (12A) are respectively left and right of the heat exchange pipe (12A). It is a flat surface perpendicular to both sides.

  In the case of the modification shown in FIG. 13 (c), the horizontal cross-sectional shape of the front and rear surfaces of the drainage promotion member (30B) is a V shape in which the central portion in the left-right direction protrudes outward in the front-rear direction.

  In the case of the modification shown in FIG. 13 (d), the horizontal cross-sectional shape of the outer surface of the rear end wall of the front heat exchange pipe (12B) is a V-shape with the central part in the left-right direction protruding rearward. The horizontal cross-sectional shape of the outer surface of the front end wall of the heat exchange pipe (12B) is V-shaped with the center portion in the left-right direction protruding forward.

  In the modification shown in FIG. 13 (e), the drainage promotion member (30B) is the same as that shown in FIG. 13 (c), and the front and rear heat exchange tubes (12B) are those shown in FIG. 13 (d). The same.

  In the modification shown in FIG. 13 (f), the drainage promotion member (30A) is the same as that shown in FIG. 13 (a), and the front and rear heat exchange tubes (12A) are as shown in FIG. 13 (b). The same.

  In the modification shown in FIG. 13 (g), the drainage promotion member (30B) is the same as that shown in FIG. 13 (c), and the front and rear heat exchange tubes (12A) are those shown in FIG. 13 (b). It ’s the same.

  In the modification shown in FIG. 13 (h), the drainage promotion member (30A) is the same as that shown in FIG. 13 (a), and the front and rear heat exchange tubes (12B) are those shown in FIG. 13 (d). The same.

  In the modification shown in FIG. 13, all the drainage promotion members (30) (30A) (30B) are made of aluminum and have a hollow shape. Further, the thickness in the left-right direction of the heat exchange tubes (12), (12A), and (12B) is equal to the thickness in the left-right direction of the drainage promotion members (30), (30A), and (30B). Furthermore, the conditions described in the first embodiment, that is, the thickness in the left-right direction of the heat exchange pipes (12) (12A) (12B) and the drainage promotion members (30) (30A) (30B) are set to h (mm). When the width in the front-rear direction of the narrowest part is w (mm), it is preferable that the relationship 0 <w / h ≦ 1/4 is satisfied.

  As in the case of the second embodiment, FIG. 14 shows that the heat exchange pipe and the drainage promotion member are in contact with each other, and between the front and rear heat exchange pipes (12) and the drainage promotion member (30), Deformation in the case where a recess (90) that is recessed inward in the left-right direction and extends in the up-down direction from the extended surfaces of the left and right sides of (12) is formed, and this recess (90) is a drainage channel (80) It is an example. In the description of this modification, the same components as those in the second embodiment are denoted by the same reference numerals and the description thereof is omitted.

  In the case of the modification shown in FIG. 14 (a), the horizontal cross-sectional shape of the drainage promotion member (30A) is the same as that shown in FIG. 13 (a).

  In the case of the modification shown in FIG. 14 (b), the horizontal sectional shape of the front and rear heat exchange tubes (12A) is the same as that shown in FIG. 13 (b).

  In the modification shown in FIG. 14 (c), the horizontal cross-sectional shape of the drainage promotion member (30B) is the same as that shown in FIG. 13 (c).

  In the case of the modification shown in FIG. 14 (d), the horizontal cross-sectional shape of the front and rear heat exchange tubes (12B) is the same as that shown in FIG. 13 (d).

  In the modification shown in FIG. 14 (e), the horizontal cross-sectional shapes of the drainage promotion member (30B) and the front and rear heat exchange tubes (12B) are the same as those shown in FIG. 13 (e).

  In the modification shown in FIG. 14 (f), the horizontal cross-sectional shapes of the drainage promotion member (30B) and the front and rear heat exchange pipes (12A) are the same as those shown in FIG. 13 (g).

  In the modification shown in FIG. 14 (g), the horizontal cross-sectional shapes of the drainage promotion member (30A) and the front and rear heat exchange tubes (12B) are the same as those shown in FIG. 13 (h).

In the modification shown in FIG. 14, all the drainage promotion members (30) (30A) (30B) are made of aluminum and have a hollow shape. Further, the thickness in the left-right direction of the heat exchange tubes (12), (12A), and (12B) is equal to the thickness in the left-right direction of the drainage promotion members (30), (30A), and (30B). Further, when the conditions described in the second embodiment, that is, the cross-sectional area of the drainage channel is S (mm ² ) and the thickness in the left-right direction of the heat exchange pipe (12) and the drainage promotion member 820) is h (mm), 0. It is preferable that the relationship of 05 ≦ S / h ≦ 1.5 is satisfied.

  In the first and second embodiments and the modifications shown in FIGS. 13 to 14, the drainage promotion member is hollow, but is not limited to this and may be solid.

  When the drainage promotion member is solid, drainage grooves extending in the vertical direction may be formed on at least one of the left and right side surfaces. A specific example will be described with reference to FIG.

  Drainage grooves (400) each consisting of a square groove are formed on the left and right sides of the drainage promotion member (300) in FIG. 15 (a).

  Drainage grooves (400A) each formed of a V-groove are formed on both left and right side surfaces of the drainage promotion member (300A) in FIG. 15 (b).

  A drainage groove (400B) made of an arc groove is formed on each of the left and right side surfaces of the drainage promotion member (300B) in FIG. 15 (c).

  On one side of the drainage promotion member (300C) in FIG. 15 (d), a drainage groove (400C) formed of a U-groove is formed.

  On one side of the drainage promotion member (300D) in FIG. 15 (e), a drainage groove (400D) comprising a square groove is formed.

  On one side of the drainage promotion member (300E) in FIG. 15 (f), a drainage groove (400E) composed of a V-groove is formed.

  On one side of the drainage promotion member (300F) in FIG. 15 (g), a drainage groove (400F) is formed which is formed of a deformed V-groove whose one side surface is perpendicular to the left and right side surfaces.

  In FIGS. 15 (a) to 15 (g), the horizontal cross-sectional shape of the front and rear surfaces of the drainage promotion member is an arc shape in which the central portion in the left-right direction protrudes outward in the front-rear direction, but is not limited thereto. Instead, the shape may be as shown in FIGS. 13 (a) and 13 (c).

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partially cutaway perspective view showing an overall configuration of an evaporator according to Embodiment 1 of the present invention. It is the vertical sectional view which omitted the middle part at the time of seeing the evaporator shown in Drawing 1 from back. It is a disassembled perspective view of the refrigerant | coolant inlet / outlet part of the evaporator shown in FIG. It is the AA line expanded sectional view of Drawing 2 which omitted some. It is a disassembled perspective view of the part of the tank for refrigerant | coolant turns of the evaporator shown in FIG. FIG. 3 is an enlarged sectional view taken along line B-B in FIG. 2. FIG. 3 is a partially enlarged view of FIG. 2. FIG. 5 is an enlarged sectional view taken along the line CC in which a part of FIG. 4 is omitted. It is the elements on larger scale of FIG. It is a figure which shows how the refrigerant | coolant flows in the evaporator shown in FIG. 6 is a graph showing the results of Experimental Example 1 and Comparative Experimental Example 1. It is a figure equivalent to FIG. 9 which shows the evaporator of Embodiment 2 by this invention. It is a horizontal sectional view showing a modification of a drainage promotion member and a heat exchange pipe. It is a horizontal sectional view showing other modifications of a drainage promotion member and a heat exchange pipe. It is a horizontal sectional view showing other modifications of a drainage promotion member.

Explanation of symbols

(1): Evaporator
(4): Heat exchange core
(5): Refrigerant inlet header (first header)
(6): Refrigerant outlet header (second header)
(9): Refrigerant inflow header (third header)
(11): Refrigerant outflow header (4th header)
(12) (12A) (12B): Heat exchange pipe
(13): Heat exchange tube group
(30) (30A) (30B): Drainage promotion member
(60): Drainage channel
(70): Clearance
(80): Drainage channel
(90): Recess
(300) (300A) (300B) (300C) (300D) (300E) (300F): Drainage promotion member
(400) (400A) (400B) (400C) (400D) (400E) (400F): Drain

Claims (24)

An evaporator provided with a plurality of heat exchange tubes arranged at intervals in the front-rear direction and extending in the vertical direction,
An evaporator in which a drainage promotion member extending in the vertical direction is disposed between heat exchange pipes adjacent to each other in the front and rear, and a drainage channel is formed between the front and rear heat exchange pipes and the drainage promotion member. There is a gap between at least one of the two heat exchange pipes adjacent to the front and rear and the drainage promotion member disposed between the two heat exchange pipes, and this gap serves as a drainage channel. The evaporator according to Item 1. At least one of the two heat exchange pipes adjacent to each other in front and back is in contact with the drainage promotion member disposed between the two heat exchange pipes, and the drainage promotion member and the heat exchange pipe in contact therewith 2. The evaporator according to claim 1, wherein a recess that is recessed inward in the left-right direction and extends in the up-down direction is formed from the extended surfaces of the left and right side surfaces of the heat exchange pipe, and the recess serves as a drainage channel. The evaporator according to any one of claims 1 to 3, wherein the heat exchange pipe has a flat shape and is disposed with its width direction directed in the front-rear direction. The evaporator according to any one of claims 1 to 4, wherein a drainage groove extending in the vertical direction is formed on at least one of the left and right side surfaces of the drainage promotion member. The evaporator according to claim 1, wherein the heat exchange pipe is flat and is arranged with its width direction directed in the front-rear direction, and the thickness in the left-right direction of the drainage promotion member is equal to the thickness in the left-right direction of the heat exchange pipe. . There is a gap between at least one of the two heat exchange pipes adjacent to the front and rear and the drainage promotion member disposed between the two heat exchange pipes, and this gap serves as a drainage channel. The pipe and the drainage promotion member satisfy the relationship of 0 <w / h ≦ 1/4, where h (mm) is the thickness in the left-right direction and w (mm) is the width in the front-rear direction of the drainage channel. Evaporator. At least one of the two heat exchange pipes adjacent to each other in front and back is in contact with the drainage promotion member disposed between the two heat exchange pipes, and the drainage promotion member and the heat exchange pipe in contact therewith Between the left and right sides of the heat exchange pipe, a recess that is recessed inward in the left-right direction and extending in the up-down direction is formed as a drainage channel. The evaporator according to claim 6, satisfying a relationship of 0.05 ≦ S / h ≦ 1.5, where (mm ² ), and the thickness in the left-right direction of the heat exchange pipe and the drainage promotion member is h (mm). The evaporator according to any one of claims 6 to 8, wherein the horizontal cross-sectional shapes of the end wall outer surface on the drainage promotion member side in the front and rear heat exchange pipes and the front and rear surfaces of the drainage promotion member are respectively arcuate. The horizontal cross-sectional shape of one of the outer wall of the drainage promotion member side of the front and rear heat exchange pipes and the front and rear surfaces of the drainage promotion member is an arc, and the other is perpendicular to the left and right side surfaces of the heat exchange pipe. The evaporator according to any one of claims 6 to 8, which is a flat surface. The horizontal cross-sectional shape of any one of the end wall outer surface on the drainage promotion member side in the front and rear heat exchange pipes and the front and rear surfaces of the drainage promotion member is an arc shape, and the other horizontal cross-sectional shape is a V shape. The evaporator in any one of -8. The evaporator according to any one of claims 6 to 8, wherein the horizontal cross-sectional shapes of the end wall outer surface on the drainage promotion member side in the front and rear heat exchange pipes and the front and rear surfaces of the drainage promotion member are respectively V-shaped. The horizontal cross-sectional shape of one of the outer wall of the drainage promotion member side of the front and rear heat exchange pipes and the front and rear faces of the drainage promotion member is V-shaped, and the other is perpendicular to the left and right side surfaces of the heat exchange pipe. The evaporator according to any one of claims 6 to 8, which is a flat surface. There is a gap between at least one of the two heat exchange pipes adjacent to the front and rear and the drainage promotion member disposed between the two heat exchange pipes, and this gap serves as a drainage channel. When the horizontal thickness of the pipe and the drainage promotion member is h (mm) and the width in the front-rear direction of the drainage channel is w (mm), the relationship 0 <w / h ≦ 1/4 is satisfied and the drainage channel faces the drainage channel. The evaporator according to claim 6, wherein the outer surface of the end wall of the heat exchange pipe and the outer surface of the drainage promotion member facing the drainage path are flat surfaces that are perpendicular to the left and right side faces of the heat exchange pipe. The evaporator according to any one of claims 6 to 14, wherein a drainage groove extending in a vertical direction is formed on at least one of the left and right side surfaces of the drainage promotion member. A heat exchange tube group composed of a plurality of heat exchange tubes arranged at intervals in the left-right direction is arranged in a plurality of rows at intervals in the front-rear direction, and A first header arranged on one end side and connected to a heat exchange pipe of at least one row of heat exchange pipe groups; arranged on the rear side of the first header on one end side of the heat exchange pipe; and the remaining heat exchange A second header to which a heat exchange pipe of the tube group is connected; a third header to which the heat exchange pipe connected to the first header is connected to the other end of the heat exchange pipe; and a heat exchange pipe And the fourth header to which the heat exchange pipe of the heat exchange pipe group connected to the second header is connected, and between the heat exchange pipes adjacent to each other, The drainage promotion member extended in the up-down direction is described in any one of Claims 1-15 Evaporator. The evaporator according to claim 16, wherein the first header and the second header are integrated. The first header and the second header form a part on the heat exchange pipe side of both headers, and the first member to which the heat exchange pipe is connected, and a part on the opposite side of the heat exchange pipe in both headers. The evaporator according to claim 17, further comprising a second member brazed to the first member, whereby both headers are integrated. The evaporator according to any one of claims 16 to 18, wherein the third header and the fourth header are integrated. The third header and the fourth header form a part on the heat exchange pipe side of both headers and the first member to which the heat exchange pipe is connected and the part on the opposite side of the heat exchange pipe in both headers. The evaporator according to claim 19, further comprising: a second member brazed to the first member, whereby both headers are integrated. The first header is a refrigerant inlet header having a refrigerant inlet, the second header is a refrigerant outlet header having a refrigerant outlet, and the third header is a refrigerant in which the refrigerant flows from the refrigerant inlet header through the heat exchange pipe. 21. The inflow header, the fourth header is a refrigerant outflow header through which the refrigerant flows out to the refrigerant outlet header through the heat exchange pipe, and the third header and the fourth header are in communication with each other. The evaporator as described in any one of them. A refrigeration cycle comprising a compressor, a condenser, and an evaporator, and using a chlorofluorocarbon refrigerant, wherein the evaporator is an evaporator according to any one of claims 1 to 21. A compressor, a gas cooler, an evaporator, a decompressor, and a refrigeration cycle that includes an intermediate heat exchanger that exchanges heat between the refrigerant that has come out of the gas cooler and the refrigerant that has come out of the evaporator, and uses a supercritical refrigerant, The supercritical refrigerating cycle which an evaporator consists of an evaporator in any one of Claims 1-21. A vehicle in which the refrigeration cycle according to claim 22 or 23 is mounted as a car air conditioner.

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