JP2006170601A - Evaporator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an evaporator having superior discharging performance of condensation water generated on a surface of a fin. <P>SOLUTION: This evaporator 1 comprises a plurality of flat heat exchange tubes 12 arranged in a left-right direction at a spacing with the widthwise direction thereof pointing forward or rearward, and corrugate fins 14 arranged between respective adjacent pairs of heat exchange tubes 12. At least a front edge portion of front and rear both side edge portions of the corrugate fin 14 is projected forwardly outward beyond the heat exchange tubes 12. Assuming that the amount of projection of the fins 14 beyond the heat exchange tubes 12 is X mm and that the heat exchange tubes 12 are Y mm in thickness in the left-right direction as a height of the heat exchange tube 12, X and Y have the relationship of 0.11Y≤X≤1.0Y. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

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

  In this specification and claims, the downstream side (the direction indicated by the arrow X in FIGS. 1, 3, and 6) of the air flowing through the ventilation gap between adjacent heat exchange tubes is forward and the opposite side thereof. Let's call it after. In addition, the top and bottom, left and right (up and down, left and right in FIG. 2) when viewing the front from the back are referred to as top and bottom and left and right.

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

  And as an evaporator satisfying such a requirement, the present applicant has previously arranged two rows of heat exchange tube groups consisting of a plurality of heat exchange tubes arranged at intervals in the front-rear direction, A heat exchange core part formed by arranging corrugated fins with louvers between adjacent heat exchange pipes, a refrigerant inlet / outlet tank arranged on the upper end side of the heat exchange core part, and a lower end side of the heat exchange core part A refrigerant turn tank, and the refrigerant inlet / outlet tank is partitioned by a partition wall into a refrigerant inlet header portion located on the front side and a refrigerant outlet header portion located on the rear side, and the refrigerant inlet header portion A refrigerant inlet is formed at one end of the refrigerant outlet, a refrigerant outlet is formed at the same end as the refrigerant inlet in the refrigerant outlet header, and the refrigerant turn tank is located on the front side by the partition wall And a refrigerant outflow header portion located on the rear side, and a plurality of refrigerant passage holes are formed in the partition wall of the refrigerant turn tank at intervals in the length direction, and the heat exchange tubes of the heat exchange tube group on the front side Is connected to the refrigerant inlet header, the upper end of the heat exchange pipe of the rear heat exchange pipe group is connected to the refrigerant outlet header part, and the lower end of the heat exchange pipe of the front heat exchange pipe group flows into the refrigerant. The lower end of the heat exchange pipe of the rear heat exchange pipe group is connected to the header, the refrigerant outflow header part, and the refrigerant flowing into the refrigerant inlet header part of the refrigerant inlet / outlet tank is transferred to the front heat exchange pipe group. It flows into the refrigerant inflow header part of the refrigerant turn tank through the heat exchange pipe, then into the refrigerant outflow header part through the refrigerant passage hole of the partition wall, and further, the heat exchange pipe of the rear heat exchange pipe group To flow into the refrigerant outlet header of the refrigerant inlet / outlet tank It proposed an evaporator which is (see Patent Document 1).

However, since the evaporator described in Patent Document 1 is reduced in size, weight, and performance, a larger amount of condensed water is generated on the surface of the corrugated fin than in the conventional laminated evaporator, and the unit of the evaporator. There is a possibility that the amount of condensed water per volume increases, and as a result, the condensed water scatters, or the condensed water freezes on the surface of the corrugated fins and the heat exchange performance decreases. By the way, in an evaporator, the condensed water generated on the fin surface usually drops through a gap between adjacent louvers, and the length of the louver may be increased to improve drainage. However, as in the evaporator of Patent Document 1, in order to reduce the size and weight, it is necessary to reduce the interval between adjacent heat exchange tubes, so there is a limit to increasing the louver length.
Japanese Patent Laid-Open No. 2003-75024

  An object of the present invention is to provide an evaporator that solves the above problems and has excellent drainage of condensed water generated on the surface of the fin.

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

1) In an evaporator provided with a plurality of flat heat exchange tubes arranged at intervals in the left-right direction so that the width direction faces the front-rear direction, and fins arranged between adjacent heat exchange tubes,
An evaporator in which at least the front side edge of the front and rear side edges of the fin protrudes forward from the heat exchange pipe.

  2) The evaporator according to 1) above, wherein only the front edge of the fin protrudes forward from the heat exchange tube.

  3) The above 1) satisfying the relationship of 0.11Y ≦ X ≦ 1.0Y, where Xmm is the amount of protrusion of the fin from the heat exchange tube and Ymm is the thickness of the heat exchange tube in the left-right direction. 2) The evaporator described.

  4) The above 1) satisfying the relationship of 0.3Y ≦ X ≦ 0.8Y, where Xmm is the amount of protrusion of the fin from the heat exchange tube and Ymm is the thickness of the heat exchange tube in the left-right direction. 2) The evaporator described.

  5) The end face of the heat exchange tube on the side from which the fin protrudes is a partial cylindrical surface in which a central portion in the tube height direction protrudes outward in the cross section, according to any one of 1) to 4) above Evaporator.

  6) The evaporator according to any one of the above items 1) to 4), wherein the end surface of the heat exchange tube on the side from which the fin protrudes is a flat surface perpendicular to both the left and right side surfaces.

  7) The evaporator according to 6) above, wherein a connecting portion between the end surface of the heat exchange pipe on which the fin protrudes and the left and right side surfaces are rounded.

  8) The fin is composed of a corrugated fin including a wave crest portion, a wave bottom portion and a connecting portion connecting the wave crest portion and the wave bottom portion, and a plurality of louvers arranged in the ventilation direction at the connecting portion, and the fin protrudes The evaporator according to any one of the above 1) to 7), wherein the louver located at the end portion of the heat exchange pipe is located on the inner side in the front-rear direction than the end of the heat exchange pipe on which the fin protrudes.

  9) The evaporator according to 8) above, wherein the distance between the louver located at the end portion on the side where the fin protrudes and the end on the side where the fin protrudes in the heat exchange tube is 1 mm or less.

  10) The above-mentioned 8) or 9), wherein the linear distance between the wave crest and the wave bottom, which is the fin height, is 7.0 mm to 10.0 mm, and the pitch of the connecting portion, which is also the fin pitch, is 1.3 to 1.8 mm. The described evaporator.

  11) The corrugated fin has a wave crest and a wave bottom formed of a flat portion and a rounded portion provided on both sides of the flat portion and connected to the connecting portion, and the radius of curvature of the rounded portion is 0.7 mm or less. The evaporator according to any one of 8) to 10).

  12) The evaporator according to any one of 1) to 11) above, wherein the pipe height, which is the thickness of the heat exchange pipe, is 0.75 to 1.5 mm.

  13) It comprises a plurality of heat exchange tubes arranged in the left-right direction and arranged in rows in the front-rear direction, and fins are provided in all heat exchange tubes. The evaporator according to any one of the above 1) to 12), which is disposed between adjacent heat exchange tubes so as to straddle.

  14) A refrigerant inlet header portion arranged on the front side on one end side of the heat exchange tube and connected to at least one row of heat exchange tube groups, and arranged on the rear side of the refrigerant inlet header portion on one end side of the heat exchange tube. And a refrigerant outlet header part to which the remaining heat exchange pipe group is connected, and a first intermediate to which a heat exchange pipe arranged on the other end side of the heat exchange pipe and connected to the refrigerant inlet header part is connected. A header portion and a second intermediate header portion disposed on the rear side of the first intermediate header portion on the other end side of the heat exchange tube and connected to a heat exchanger tube connected to the refrigerant outlet header portion; The evaporator according to 13) above, wherein both of the intermediate header portions are in communication with each other.

  15) The evaporator according to 14) above, wherein the refrigerant inlet header section, the refrigerant outlet header section, and the two intermediate header sections are each formed by partitioning one tank in the front-rear direction by partition means.

  16) A refrigeration cycle comprising a compressor, a condenser, and an evaporator, wherein the evaporator is the evaporator according to any one of 1) to 15) above.

  17) A vehicle in which the refrigeration cycle described in 16) above is mounted as an air conditioner.

  According to the evaporators of the above 1), 2) and 5) to 7), at least one of the front and rear side edges of the fin protrudes outward in the front-rear direction from the heat exchange pipe. Corners are formed between the left and right edges of the end surface of the fin on the protruding side of the fin and the protruding portion of the fin, and the condensed water generated on the surface of the fin enters the above by surface tension. It flows so as to be drawn to the corner portion, and then flows downward along the corner portion and the end face of the heat exchange pipe. Therefore, the drainage of the condensed water generated on the fin surface is improved, and the deterioration of the heat exchange performance due to the scattering of the condensed water and the freezing of the condensed water is prevented. In particular, the condensed water generated on the fin surface is easy to flow to the downstream side of the ventilation direction by the wind flowing through the ventilation gap between adjacent heat exchange tubes, that is, the front side. Is.

  According to the evaporators 3) and 4), the drainage of the condensed water generated on the fin surface is reliably improved, and according to the evaporator 4), the drainage of the condensed water is further improved.

  According to the evaporator of 8) above, the louver located at the end on the side where the fin protrudes is located on the inner side in the front-rear direction than the end on the side where the fin protrudes in the heat exchange tube. The generated condensed water is smoothly drawn to the corner portion by the surface tension, and the drainage performance is improved. That is, the condensed water generated on the upper surface of the connecting portion of the corrugated fin passes through the gap between the adjacent louvers, reaches the surface of the heat exchange tube through the lower surface of the connecting portion, and follows the junction between the surface of the heat exchanger tube and the corrugated fin. The surface tension is smoothly drawn to the corner. If the louver located at the end on the side where the fin protrudes is located on the outer side in the front-rear direction with respect to the end face of the heat exchange tube, there is a possibility that condensed water may stay in the louver portion.

  According to the evaporator of 9), the effect of 8) is most excellent.

  According to the evaporator of the above 10), it is possible to improve the heat exchange performance while suppressing an increase in ventilation resistance and to improve the balance between the two.

  According to the evaporator of the above 11), it is possible to improve the heat exchange performance while suppressing an increase in ventilation resistance and to improve the balance between the two.

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

  1 and 2 show the overall configuration of an evaporator for a car air conditioner according to the present invention, and FIGS. 3 to 8 show the configuration of the main part.

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

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

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

  As shown in FIG. 3 and FIG. 4, the refrigerant inlet / outlet tank (2) is formed of a plate-shaped first member (formed from a brazing aluminum sheet having a brazing filler metal layer on both sides and connected to a heat exchange pipe (12)). 16), a second member (17) made of a bare material formed from an aluminum extruded shape and covering the upper side of the first member (16), and an aluminum brazing sheet having a brazing filler metal layer on both sides. It consists of aluminum caps (18) and (19) which are joined to both ends of the members (16) and (17) to close the opening on both the left and right sides, and on the outer surface of the right cap (19), the refrigerant inlet header (5) and the refrigerant An aluminum pipe joint plate (21) that is long in the front-rear direction is brazed so as to straddle the outlet header portion (6). A refrigerant inlet pipe (7) and a refrigerant outlet pipe (8) are connected to the pipe joint plate (21).

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

  The second member (17) has a substantially m-shaped cross section that opens downward, and is provided in the center between the front and rear walls (26) extending in the left-right direction and the front and rear walls (26) and extends in the left-right direction. In addition, the partition wall (27) as a partitioning means for partitioning the refrigerant inlet / outlet tank (2) into two front and rear spaces, and the upper ends of the front and rear walls (26) and the upper ends of the partition walls (27) are integrally connected. And two substantially arc-shaped connecting walls (28) projecting from each other. 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 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 left cap (18), a right protruding portion (32) that is fitted into the refrigerant inlet header portion (5) is integrally formed, and on the rear side, the refrigerant outlet header portion (6) is divided. The upper right protrusion (33) that fits in the space (6a) above the diversion resistor plate (29) and the lower fit in the space (6b) below the diversion resistor plate (29) The side right protrusion (34) is integrally formed with an interval in the vertical direction. In addition, engaging claws (35) protruding rightward are integrally formed on the arc-shaped portion between the front and rear side edges and the upper edge of the left cap (18). Further, an engaging claw (36) protruding rightward is formed integrally with the front side portion and the rear side portion of the lower edge of the left cap (18). The right cap (19) is symmetrical with the left cap (18) and has a left-side protruding portion (37) fitted into the refrigerant inlet header portion (5) and a shunt resistor plate for the refrigerant outlet header portion (6). Upper left protrusion (38) that fits in the space (6a) above (29) and lower left that fits in the space (6b) below the shunt resistor plate (29) The protruding portion (39) and the upper and lower engaging claws (41) (42) are integrally formed. A refrigerant inlet (43) is formed in the bottom wall of the front left protrusion (37) of the right cap (19), and a refrigerant outlet (44) is also formed in the bottom wall of the rear upper left protrusion (38). Is formed.

  The pipe joint plate (21) includes a short cylindrical refrigerant inlet (45) leading to the refrigerant inlet (43) of the right cap (19) and a short cylindrical refrigerant outlet (46) also leading to the refrigerant outlet (44). Are integrally formed. The outer diameter of the refrigerant inlet (45) is smaller than the outer diameter of the refrigerant outlet (46). A reduced diameter portion formed at one end of the refrigerant inlet pipe (7) is inserted into the refrigerant inlet (45) of the pipe joint plate (21) and brazed, and the refrigerant outlet is also connected to the refrigerant outlet (46). A reduced diameter portion formed at one end of the tube (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) of the refrigerant inlet / outlet tank (2), the caps (18), (19), and the pipe joint plate (21) 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 (32) and (37) are in the space on the front side of the partition walls (27) in both members (16) and (17), and the rear upper protrusions ( 33) (38) is located behind the partition wall (27) in both members (16) and (17) and above the shunting resistance plate (29), and the rear lower protrusion (34 ) (39) are respectively fitted in the spaces behind the partition wall (27) and below the shunt resistor plate (29), and the upper engaging claws (35) (41) are second In a state where the lower engaging claws (36) and (42) are engaged with the curved portion (22) of the first member (16) while being engaged with the connecting wall (28) of the member (17), The first and second members 16 and 17 are brazed using the brazing material layers of both caps 18 and 19. The pipe joint plate (21) is brazed to the right cap (19) using the brazing material layer of the right cap (19). Thus, the refrigerant inlet / outlet tank (2) is formed, the refrigerant inlet header portion (5) on the front side of the partition wall (27) of the second member (17) and the refrigerant on the rear side of the partition wall (27). It is the exit header (6). The refrigerant outlet header (6) is divided into upper and lower spaces (6a) and (6b) by a shunt resistor plate (29), and these spaces (6a) and (6b) are formed in the refrigerant passage holes (31A) ( 31B). The refrigerant outlet (44) of the right cap (19) communicates with the upper space (6a) of the refrigerant outlet header (6). Further, the refrigerant inlet (45) and the refrigerant outlet (46) of the pipe joint plate (21) are communicated with the refrigerant inlet (43) and the refrigerant outlet (44), respectively.

  As shown in FIGS. 3 and 5, the refrigerant turn tank (3) is formed of an aluminum brazing sheet having a brazing filler metal layer on both sides and a plate-shaped first member (12) connected to a heat exchange pipe (12). 48), a second member (49) made of a bare material formed from an extruded aluminum material and covering the lower side of the first member (48), an aluminum brazing sheet having a brazing filler metal layer on both sides and It consists of an aluminum cap (51) that closes both left and right openings.

  The top surface (3a) of the refrigerant turn tank (3) has a central portion in the front-rear direction as the highest portion (52) and gradually decreases from the highest portion (52) toward the front and rear sides. The cross section is formed in a circular arc shape. Grooves (53) extending from the front and rear sides of the highest portion (52) on the top surface (3a) to the front and rear sides (3b) are spaced at the left and right sides of the front and rear sides of the refrigerant turn tank (3). A plurality are formed.

  The first member (48) has a cross-sectional arc shape in which a central portion in the front-rear direction protrudes upward, and a hanging wall (48a) is integrally formed over the entire length at both front and rear side edges. The upper surface of the first member (48) is the top surface (3a) of the refrigerant turn tank (3), and the outer surface of the hanging wall (48a) is the front and rear side surfaces (3b) of the refrigerant turn tank (3). ing. On both the front and rear sides of the first member (48), a groove (53) is formed from the highest position (52) at the center in the front-rear direction to the lower end of the hanging wall (48a). A long tube insertion hole (54) is formed in the front-rear direction between adjacent grooves (53) in the front and rear side portions excluding the highest portion (52) of the first member (48). The front and rear pipe insertion holes (54) are at the same position in the left-right direction. A plurality of through holes (55) are formed in the highest position (52) of the first member (48) at intervals in the left-right direction. The first member (48) is formed by simultaneously forming a hanging wall (48a), a groove (53), a tube insertion hole (54) and a through hole (55) by pressing an aluminum brazing sheet. .

  The second member (49) has a substantially w-shaped cross section opened upward, and extends between the front and rear walls (56) extending in the left-right direction and curved upward toward the outer side in the front-rear direction, and the front and rear walls (56). A vertical partition wall (57) as a partition means provided in the center and extending in the left-right direction and partitioning the refrigerant turn tank (3) into two front and rear spaces, and both front and rear walls (56) and partition walls ( 57) and two connecting walls (58) for connecting the lower ends of the two together. The upper end of the partition wall (57) protrudes upward from the upper ends of the front and rear walls (56), and the upper edge protrudes upward and is fitted into the through hole (55) of the first member (48). The protrusions (57a) are integrally formed at intervals in the left-right direction. In addition, a refrigerant passage notch (57b) is formed from the upper edge between adjacent protrusions (57a) in the partition wall (57). The protrusion (57a) and the notch (57b) are formed by cutting a predetermined portion of the partition wall (57).

  The second member (49) is formed by integrally extruding the front and rear walls (56), the partition wall (57), and the connecting wall (58), and then cutting the partition wall (57) to form a protrusion (57a) and a notch Manufactured by forming (57b).

  On the front side of each cap (51), a protruding portion (59) inward in the left-right direction that is fitted into the refrigerant inflow header portion (9) is integrally formed, and on the rear side, the refrigerant outflow header portion ( 11) A projecting portion (61) inward in the left-right direction, which is fitted in, is integrally formed. In addition, an engaging claw (62) projecting inward in the left-right direction is integrally formed on the arc-shaped portion between the front and rear side edges and the lower edge of each cap (51), and is also formed in the left-right direction in the upper edge. A plurality of engaging claws (63) projecting in the direction are integrally formed at intervals in the front-rear direction.

  The first and second members (48), (49) of the refrigerant turn tank (3) and the caps (51) are brazed as follows. The first and second members (48) and (49) are drooped before and after the first member (48) by the projection (57a) of the second member (49) being inserted into the through hole (55) and caulked. With the lower end of the wall (48a) engaged with the upper end of the front and rear walls (56) of the second member (49), the brazing material layer of the first member (48) is used to braze each other. It is attached. Both caps (51) have a front protrusion (59) in the space in front of the partition wall (57) in both members (48) and (49), and a rear protrusion (61) in both members (48). ) (49) are respectively fitted into the spaces behind the partition wall (57), and the upper engaging claw (63) is engaged with the first member (48), so that the lower engaging claw is engaged. With the (62) engaged with the front and rear walls (56) of the second member (49), the brazing material layer of each cap (51) is used to make the first and second members (48) (49). ) Is brazed. Thus, the refrigerant turn tank (3) is formed, the refrigerant inflow header portion (9) on the front side of the partition wall (57) of the second member (49), and the refrigerant on the rear side of the partition wall (57). It is an outflow header (11). The upper end opening of the notch (57b) of the partition wall (57) of the second member (49) is closed by the first member (48), thereby forming a refrigerant passage hole (64).

  As shown in FIGS. 6 and 7, the heat exchange pipe (12) constituting the front and rear heat exchange pipe group (13) is a flat shape made of an extruded aluminum material, and its width direction faces the front-rear direction. They are arranged at intervals in the left-right direction. A plurality of refrigerant passages (12a) extending in the length direction are formed in parallel in the heat exchange pipe (12). The front and rear end faces of the heat exchange tube (12) are partial cylindrical surfaces in which the central portion in the tube height direction, which is the thickness in the left-right direction in the cross section, protrudes outward. The upper end of the heat exchange pipe (12) is inserted into the pipe insertion hole (23) of the first member (16) of the refrigerant inlet / outlet tank (2), and the brazing material layer of the first member (16) is used. The first member (48) is brazed to the first member (48), and the lower end of the first member (48) is inserted into the pipe insertion hole (54) of the first member (48) of the refrigerant turn tank (3). ) Is brazed to the first member (48) using the brazing material layer.

  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 end faces The curvature radius 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 portions formed by rolling on the brazing filler metal layer side of an aluminum brazing sheet having a brazing filler metal layer on one side and connected via a connecting portion, and connection in each flat wall forming portion A side wall forming portion integrally formed in a raised shape from the side edge opposite to the portion, and a plurality of integrally formed in a raised shape from both flat wall forming portions at a predetermined interval in the width direction of the flat wall forming portion. A plate provided with a partition wall forming portion may be bent into a hairpin shape at the connecting portion, the side wall forming portions are brought into contact with each other and brazed to each other, and a partition wall is formed by the partition wall forming portion.

  The corrugated fin (14) is formed in a corrugated shape using an aluminum brazing sheet having a brazing filler metal layer on both sides, and connects the wave crest and wave bottom and is a substantially horizontal connecting portion (14a) extending in the front-rear direction. In addition, a plurality of louvers (65) are formed in parallel at intervals in the front-rear direction. The corrugated fin (14) is shared by the front and rear heat exchange tube groups (13). The front edge of the corrugated fin (14) protrudes forward (outward in the front-rear direction) from the front end of the heat exchange pipe (12) of the front heat exchange pipe group (13), and the rear edge is also the rear heat exchange. It projects rearward (outward in the front-rear direction) from the rear end of the heat exchange tube (12) of the tube group (13). These protrusions are indicated by (14b). In this case, between the front end face of the heat exchange pipe (12) of the front heat exchange pipe group (13) and the protrusion (14b) forward of the corrugated fin (14), and the rear heat exchange pipe group (13) Corner portions (66) are formed between the rear end face of the heat exchange pipe (12) and the rearward projecting part (14b) of the corrugated fin (14), and the corrugated fin (14) The condensed water generated on the surface flows so as to be attracted to the entering corner portion (66) by the surface tension, and then flows downward along the entering corner portion (66) and the end face of the heat exchange pipe (12). Accordingly, the drainage of the condensed water generated on the surface of the corrugated fin (14) is improved, and the deterioration of the heat exchange performance due to the scattering of the condensed water and the condensation water freezing is prevented. The condensed water generated on the surface of the corrugated fin (14) is easy to flow downstream in the ventilation direction, that is, on the front side by the wind flowing through the ventilation gap between the adjacent heat exchange tubes (12). Only the front edge of (14) protrudes forward from the front end of the heat exchange pipe (12), and the rear edge of the corrugated fin (14) is heat exchange of the rear heat exchange pipe group (13). For example, it may be located in the same vertical plane as the central portion of the rear end surface of the heat exchange tube (12) in the left-right direction, rather than projecting rearward from the rear end of the tube (12). When the rear edge of the corrugated fin (14) is located in front of the rear end of the heat exchange pipe (12) of the rear heat exchange pipe group (13), the corrugated fin in the heat exchange pipe (12) Condensation water may freeze on the surface of the portion where (14) does not exist.

  As shown in FIG. 8, when the projection amount of the corrugated fin (14) from the heat exchange pipe (12) is Xmm and the pipe height, which is the thickness in the left-right direction of the heat exchange pipe (12), is Ymm. It is preferable that the relationship 11Y ≦ X ≦ 1.0Y is satisfied, and it is preferable that the relationship 0.3Y ≦ X ≦ 0.8Y is satisfied. In the case of X <0.11Y and X> 1.0Y, the drainage of the condensed water generated on the surface of the corrugated fin (14) may not be sufficient. The louver (65) located at the end of the corrugated fin (14) on the protruding portion (14b) side is located on the inner side in the front-rear direction than the end of the heat exchange tube (12) on the protruding portion (14b) side. The distance Z between the louver (65) and the end of the heat exchange tube (12) on the protruding portion (14b) side is preferably 1 mm or less.

  Here, the linear distance between the wave top and the wave bottom which is the fin height (H) of the corrugated fin (14) is 7.0 mm to 10.0 mm, and the pitch of the connecting portion (14a) which is also the fin pitch (P). Is preferably 1.3 to 1.8 mm. The corrugated fin (14) has a wave crest and a wave bottom that are flatly brazed to the heat exchange pipe (12) and are rounded on both sides of the flat part and connected to the connecting portion (14a). The radius of curvature (R) of the rounded portion is preferably 0.7 mm or less (see FIG. 7). In addition, instead of sharing one corrugated fin between the front and rear heat exchange tube groups (13), corrugated fins are respectively arranged between adjacent heat exchange tubes (12) of both heat exchange tube groups (13). It may be. In this case, at least the front edge of the front and rear side edges of the corrugated fin (14) disposed between the adjacent heat exchange pipes (12) of each heat exchange pipe group (13) is more or less than the heat exchange pipe. Protruding outward in the direction.

  The relationship between the protrusion amount Xmm of the corrugated fin (14) from the heat exchange pipe (12) and the pipe height Ymm which is the thickness in the left-right direction of the heat exchange pipe (12) is 0.11Y ≦ X ≦ 1.0Y It is preferable to do this from the results of the following experiments conducted by the present inventors.

  That is, an evaporator having a heat exchange tube (12) with a tube height (h) of 1.4 mm, a tube width of 17 mm, a fin height (H) of 8 mm, and a fin pitch (P) of 1.5 mm is used. The airflow resistance at the time of measuring the thermal performance was measured by a test method according to JIS D1618, and the relationship between the protrusion amount of the corrugated fin (14) from the heat exchange pipe (12) and the airflow resistance was obtained. The increase in ventilation resistance means that the condensed water generated on the surface of the fin (14) is not drained efficiently. The result is shown in FIG. The airflow resistance in the graph shown in FIG. 9 indicates a ratio when the protrusion amount is 0 as a reference (100%). From the graph shown in FIG. 9, the ventilation resistance of 98% or less, which is considered to be efficiently drained of the condensed water, is the case where the protrusion amount is 0.154 mm or more and 1.4 mm or less, In this case, it is understood that the condensed water is drained and the ventilation resistance is reduced. Here, since the tube height is 1.4 mm, the protrusion amount Xmm of the corrugated fin (14) from the heat exchange tube (12) and the tube height Ymm which is the thickness in the left-right direction of the heat exchange tube (12). It has been found that the ventilation resistance is 98% or less when the relationship between and the above satisfies 0.11Y ≦ X ≦ 1.0Y. Further, as is apparent from the graph shown in FIG. 9, the projection amount Xmm of the corrugated fin (14) from the heat exchange pipe (12) and the pipe height Ymm which is the thickness in the left-right direction of the heat exchange pipe (12) It is more preferable that the relationship of 0.3Y ≦ X ≦ 0.8Y is satisfied, and it is desirable that the protrusion amount X is in the vicinity of 0.5Y.

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

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

  In the evaporator (1) described above, the gas-liquid mixed phase two-layer refrigerant that has passed through the compressor, the condenser, and the expansion valve flows from the refrigerant inlet pipe (7) to the refrigerant inlet (45) and the right side of the pipe joint plate (21). The refrigerant passage (12a) of all the heat exchange pipes (12) of the front heat exchange pipe group (13) is divided into the refrigerant inlet header part (5) through the refrigerant inlet (43) of the cap (19). Flows in.

  The refrigerant that has flowed into the refrigerant passages (12a) of all the heat exchange tubes (12) flows downward in the refrigerant passages (12a) and enters the refrigerant inflow header portion (9) of the refrigerant turn tank (3). . The refrigerant that has entered the refrigerant inflow header portion (9) enters the refrigerant outflow header portion (11) through the refrigerant passage hole (64) of the partition wall (57).

  The refrigerant that has entered the refrigerant outflow header section (11) is divided and flows into the refrigerant passages (12a) of all the heat exchange pipes (12) in the rear heat exchange pipe group (13), changing the flow direction. Then, it flows upward in the refrigerant passage (12a) and enters the lower space (6b) of the refrigerant outlet header (6). Here, resistance is imparted to the refrigerant flow by the shunt resistor plate (29), so that the shunt flow from the refrigerant outflow header (11) to the heat exchange pipe (12) of the rear heat exchange pipe group (13) is reduced. In addition to being uniformed, the flow from the refrigerant inlet header (5) to the heat exchange pipe (12) of the front heat exchange pipe group (13) is further uniformized. As a result, the refrigerant circulation amount of the heat exchange pipe (12) of both heat exchange pipe groups (13) is made uniform.

  Next, the refrigerant enters the upper space (6a) of the refrigerant outlet header (6) through the refrigerant passage holes (31A) and (31B) of the shunt resistor plate (29), and enters the refrigerant outlet of the right cap (19) ( 44) and the refrigerant outlet (46) of the pipe joint plate (21), and flows out to the refrigerant outlet pipe (8). The refrigerant passes through the refrigerant passage (12a) of the heat exchange tube (12) of the front heat exchange tube group (13) and the refrigerant passage (12a) of the heat exchange tube (12) of the rear heat exchange tube group (13). During the flow, the ventilation gap exchanges heat with the air flowing in the direction indicated by the arrow X in FIG.

  At this time, condensed water is generated on the surface of the corrugated fin (14). This condensed water is formed between the front end face of the heat exchange pipe (12) of the front heat exchange pipe group (13) and the protrusion (14b) forward of the corrugated fin (14), and the rear heat exchange pipe group ( The heat exchange pipe (12) of 13) flows so as to be attracted to the corners (66) formed between the rear end surface of the corrugated fin (14) and the projecting part (14b) to the rear of the corrugated fin (14). It flows down through the corner portion (66) and the end face of the heat exchange pipe (12), and flows down to the top surface (3a) of the refrigerant turn tank (3). The condensed water flowing down to the top surface (3a) of the refrigerant turn tank (3) enters the groove (53) by the capillary effect, flows in the groove (53), and flows from the outer end in the front-rear direction to the refrigerant turn tank. Drop down (3). In this way, freezing of condensed water due to accumulation of a large amount of condensed water between the top surface (3a) of the refrigerant turn tank (3) and the lower end of the corrugated fin (14) is prevented, and as a result, the evaporator (1 ) Performance degradation is prevented.

  FIG. 10 shows another embodiment of the evaporator.

  In the case of the embodiment shown in FIG. 10, the rear edge of the corrugated fin (14) does not protrude rearward from the rear end of the heat exchange pipe (12) of the rear heat exchange pipe group (13), and the heat The rear end surface of the exchange pipe (12) is located in the same vertical plane as the central portion in the left-right direction. Other configurations are the same as those of the above-described embodiment, and the same components and the same parts are denoted by the same reference numerals. Since the rear end face of the heat exchange pipe (12) is a partial cylindrical surface, the rear edge of the corrugated fin (14) is the rear end face of the heat exchange pipe (12) of the rear heat exchange pipe group (13). Is located in the same vertical plane as the central portion in the left-right direction of the heat exchanger tube (12) means that the rearmost protruding portion of the rear end surface of the heat exchange pipe (12) is the same vertical as the rear edge of the corrugated fin (14). It shall mean that it is located in the plane.

  In the case of this embodiment, the condensed water generated on the surface of the corrugated fin (14) is likely to flow downstream in the ventilation direction, that is, on the front side due to the wind flowing through the ventilation gap between the adjacent heat exchange tubes (12). Therefore, even if the rear edge of the corrugated fin (14) does not protrude rearward from the rear end face of the heat exchange pipe (12) of the rear heat exchange pipe group (13), the drainage performance of the condensed water is very small. Does not affect. However, if the rear edge of the corrugated fin (14) is located in front of the rear end face of the heat exchange pipe (12) of the rear heat exchange pipe group (13), the heat exchange pipe (12) Freezing of condensed water may occur on the surface of the portion where the corrugated fin (14) does not exist.

  FIG. 11 shows a modification of the heat exchange tube.

  In the case of the heat exchange pipe (12) in FIG. 11 (a), the side from which the corrugated fin (14) protrudes, here, the front and rear end faces of the heat exchange pipe (12) are flat faces that are perpendicular to the left and right side faces. ing.

  In the case of the heat exchange pipe (12) of FIG. 11 (b), in the heat exchange pipe (12) of FIG. 11 (a), the side where the corrugated fin (14) protrudes, here both the front and rear ends of the heat exchange pipe (12). The flat surface and the connecting part between the left and right side surfaces are rounded.

  In the evaporator according to the above two embodiments, between the refrigerant inlet header (5) and the refrigerant inflow header (9) of both tanks (2) and (3), and between the refrigerant outlet header (6) and the refrigerant outflow header. One heat exchange tube group (13) is provided between each of the tanks (11), but this is not restrictive, and the refrigerant inlet header (5) of both tanks (2) (3) and the refrigerant One or two or more heat exchange pipe groups (13) may be provided between the inflow header section (9) and between the refrigerant outlet header section (6) and the refrigerant outflow header section (11). . Further, there are cases where the refrigerant inlet / outlet tank is at the bottom and the refrigerant turn tank is at the top.

  In the evaporators of the above two embodiments, the coolant turn tank (3) is formed with a groove (53) for improving drainage at a portion between adjacent heat exchange pipes (12). It is not limited to this, The groove | channel for drainage improvement may be formed in the position corresponding to each heat exchange pipe | tube (12). In this case, a groove for improving drainage is formed from the top surface (3a) of the refrigerant turn tank (3) to both the front and rear side surfaces and connected to the front and rear outer ends of the respective tube insertion holes (54).

Further, the evaporator according to the present invention includes a compressor, a gas cooler, an evaporator, an expansion valve as a decompressor, an accumulator as a gas-liquid separator, and a refrigerant that has come out of the gas cooler and has passed through the gas-liquid separator. And an intermediate heat exchanger that exchanges heat with each other, and is also used in an evaporator of a supercritical refrigeration cycle that uses a supercritical refrigerant such as CO ₂ . Such a supercritical refrigeration cycle is used as a car air conditioner in a vehicle such as an automobile.

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 which looked at 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 disassembled perspective view of the part of the refrigerant | coolant in / out tank. It is a disassembled perspective view of the part of the tank for refrigerant | coolant turns. FIG. 4 is an enlarged sectional view taken along line B-B in FIG. 3. It is an expansion perspective view which shows a part of heat exchange core part. It is the elements on larger scale of FIG. It is a graph which shows the experimental result performed in order to obtain | require the relationship between the protrusion amount Xmm from the heat exchange pipe | tube of a corrugated fin, and pipe | tube height Ymm which is the thickness of the left-right direction of a heat exchange pipe | tube. FIG. 7 is a view corresponding to FIG. 6 showing another embodiment of the evaporator according to the present invention. It is a figure equivalent to FIG. 8 which shows the modification of a heat exchange pipe.

Explanation of symbols

(1): Evaporator
(2): Refrigerant tank
(3): Refrigerant turn tank
(5): Refrigerant inlet header
(6): Refrigerant outlet header
(9): Refrigerant inflow header (intermediate header)
(11): Refrigerant outflow header (intermediate header)
(12): Heat exchange pipe
(13): Heat exchange tube group
(14): Corrugated fin
(14a): Connection part
(14b): Projection
(65): Louver

Claims (17)

In an evaporator provided with a plurality of flat heat exchange tubes arranged at intervals in the left-right direction so that the width direction faces the front-rear direction, and fins arranged between adjacent heat exchange tubes,
An evaporator in which at least the front side edge of the front and rear side edges of the fin protrudes outward in the front-rear direction from the heat exchange pipe. The evaporator according to claim 1, wherein only the front edge of the fin protrudes forward from the heat exchange pipe. 3. The relationship of 0.11Y.ltoreq.X.ltoreq.1.0Y is satisfied, where the amount of protrusion of the fin from the heat exchange tube is Xmm and the thickness of the heat exchange tube in the left-right direction is Ymm. The evaporator. 3. The relationship of 0.3Y ≦ X ≦ 0.8Y is satisfied, where X is the protrusion amount of the fin from the heat exchange tube, and Ymm is the thickness of the heat exchange tube in the left-right direction. The evaporator. The evaporator according to any one of claims 1 to 4, wherein the end surface of the heat exchange tube on the side from which the fin protrudes is a partial cylindrical surface in which a central portion in the tube height direction protrudes outward in the cross section. The evaporator according to any one of claims 1 to 4, wherein an end surface of the heat exchange tube on the side from which the fins protrude is a flat surface perpendicular to both the left and right side surfaces. The evaporator according to claim 6, wherein a connecting portion between the end face of the heat exchange pipe on the side where the fin protrudes and the left and right side faces are rounded. The fin is composed of a corrugated fin having a wave crest portion, a wave bottom portion, and a connecting portion connecting the wave crest portion and the wave bottom portion, and a plurality of louvers arranged in the ventilation direction at the connecting portion, and the side from which the fin protrudes The evaporator according to any one of claims 1 to 7, wherein the louver located at the end of the heat exchanger tube is located on the inner side in the front-rear direction than the end of the heat exchange tube on which the fin protrudes. The evaporator according to claim 8, wherein a distance between a louver located at an end portion on the side where the fin protrudes and an end on the side where the fin protrudes in the heat exchange tube is 1 mm or less. The evaporator according to claim 8 or 9, wherein a linear distance between a wave top portion and a wave bottom portion, which is a fin height, is 7.0 mm to 10.0 mm, and a pitch of connecting portions, which is also a fin pitch, is 1.3 to 1.8 mm. . 9. The corrugated fin has a wave crest and a wave bottom formed of a flat portion and a rounded portion provided on both sides of the flat portion and connected to the connecting portion, and the radius of curvature of the rounded portion is 0.7 mm or less. The evaporator in any one of -10. The evaporator according to any one of claims 1 to 11, wherein a pipe height which is a thickness of the heat exchange pipe is 0.75 to 1.5 mm. It is composed of a plurality of heat exchange tubes arranged at intervals in the left-right direction, and is provided with a heat exchange tube group provided in a plurality of rows side by side in the front-rear direction, so that the fins straddle all the heat exchange tube groups Furthermore, the evaporator in any one of Claims 1-12 arrange | positioned between adjacent heat exchange pipes. A refrigerant inlet header portion disposed on the front side on one end side of the heat exchange pipe and connected to at least one row of heat exchange pipe groups; disposed on the rear side of the refrigerant inlet header section on one end side of the heat exchange pipe; and A refrigerant outlet header portion to which the remaining heat exchange tube group is connected, and a first intermediate header portion that is disposed on the other end side of the heat exchange tube and connected to the heat exchange tube that is connected to the refrigerant inlet header portion And a second intermediate header portion, which is disposed on the rear side of the first intermediate header portion on the other end side of the heat exchange tube and connected to the heat exchange tube connected to the refrigerant outlet header portion. The evaporator according to claim 13, wherein the intermediate header portions are in communication with each other. The evaporator according to claim 14, wherein the refrigerant inlet header portion, the refrigerant outlet header portion, and the two intermediate header portions are each formed by partitioning one tank in the front-rear direction by partition means. A refrigeration cycle comprising a compressor, a condenser, and an evaporator, wherein the evaporator is an evaporator according to any one of claims 1 to 15. A vehicle in which the refrigeration cycle according to claim 16 is mounted as an air conditioner.

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