JP2011085363A - Evaporator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an evaporator having excellent drainage performance of condensation water generated on the surfaces of fins. <P>SOLUTION: The evaporator includes: a pair of header tanks arranged at an interval vertically; a plurality of flat heat exchange pipes 45 which are arranged between the both header tanks with the width direction facing the fore-and-aft direction, leaving intervals in the right/left direction and have both ends connected to the header tanks; and the corrugated fins 5 arranged between the adjacent heat exchange pipes 45. Inclination parts 55 linearly inclined toward the central part in the right/left direction of the heat exchange pipe 45 outwardly in the fore-and-aft direction are provided in both right and left side portions of both front and rear end walls 45a of the heat exchange pipe 45. An angle &theta; between the inclination part 55 and both right and left side edges of the corrugated fin 5 is set to be 25-40&deg;. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

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

  In this specification and claims, the downstream side of the air flowing in the ventilation gap between adjacent heat exchange tubes (the direction indicated by the arrow X in FIGS. 1, 2, 7 and 9) The opposite side to the rear is referred to as the rear, and the upper and lower sides and the left and right in FIG.

  As an evaporator for a car air conditioner that can be reduced in size, weight, and performance, the present applicant has previously set a width direction between a pair of header tanks arranged at intervals in the vertical direction and between both header tanks. A plurality of flat heat exchange tubes made of aluminum extruded sections that are oriented in the front-rear direction and spaced apart in the length direction of the header tank and both ends are connected to the header tank, and adjacent heat exchange tubes And a corrugated fin with a louver disposed between the upper header tank and the refrigerant inlet header portion and the refrigerant outlet header portion that are provided side by side in the front-rear direction and integrated with each other, and the lower header The tank is provided on the rear side of the first intermediate header portion so as to face the refrigerant outlet header portion and the first intermediate header portion provided so as to face the refrigerant inlet header portion. And a second intermediate header portion integrated with the first intermediate header portion, and upper and lower end portions of the front heat exchange pipe are connected to the refrigerant inlet header portion and the first intermediate header portion, and also on the rear side. Proposes an evaporator in which the upper and lower ends of the heat exchange pipe are connected to the refrigerant outlet header and the second intermediate header, and the cross-sectional shape of the front and rear end walls of the heat exchange pipe is an arc shape protruding outward in the front-rear direction (See Patent Document 1).

  In the evaporator described in Patent Document 1, since a reduction in size and weight and an increase in performance are achieved, a large amount of condensed water is generated on the surface of the corrugated fin, and the amount of condensed water per unit volume of the evaporator increases. By the way, in a normal evaporator, the condensed water generated on the fin surface falls through a gap between adjacent louvers, and the length of the louver may be increased to improve drainage. However, like the evaporator of Patent Document 1, in order to reduce the size and weight, it is necessary to reduce the interval between the heat exchange tubes adjacent in the length direction of the header tank. However, if the amount of condensed water is large, drainage may be insufficient.

JP 2008-20098 A

  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 achieve the above object, the present invention comprises the following aspects.

1) A pair of header tanks arranged at intervals in the vertical direction, and between the two header tanks, the width direction is oriented in the front-rear direction and is arranged at intervals in the left-right direction, and both end portions are in the header tank An evaporator comprising a plurality of connected flat heat exchange tubes and corrugated fins arranged between adjacent heat exchange tubes,
The left and right side portions of the front and rear end walls of the heat exchange tube are provided with inclined portions that are linearly inclined outwardly in the front-rear direction toward the central portion in the left-right direction of the heat exchange tube. An evaporator having an angle of 25 to 40 degrees with the left and right side edges.

  2) Corrugated fins are in contact with the left and right side surfaces of the heat exchange tube, the width in the front-rear direction of the heat exchange tube is W1mm, and the length in the front-rear direction of the contact portion between the left and right side surfaces of the heat exchange tube and the corrugated fins The evaporator according to 1) above, wherein W2 / W1 = 80 to 95% when W2 mm is set.

  3) The evaporator according to 1) or 2) above, wherein the width of the heat exchange pipe in the front-rear direction is 10 to 20 mm.

  4) The evaporator according to any one of 1) to 3) above, wherein the thickness of the heat exchange pipe in the left-right direction is 1 to 1.8 mm.

  5) The heat exchange tube is provided in a flat hollow body in which two rectangular metal plates subjected to press working are joined in a laminated form, and both metal plates forming the flat hollow body are outward. By being bulged, a heat exchange tube having both upper and lower ends opened is provided, and both front and rear walls of the outward bulge portion forming the heat exchange tube in each metal plate are directed toward the central portion of the thickness of the flat hollow body The evaporator according to any one of 1) to 4), which is inclined linearly outward in the front-rear direction.

  6) At the front side edge of the flat hollow body, one of the two metal plates protrudes toward the corrugated fin where the other metal plate is in contact with the other metal plate rather than the other metal plate. The evaporator according to 5) above, wherein the raised ridge is formed over the entire length.

  According to the evaporators 1) to 6), the right and left side portions of the front and rear end walls of the heat exchange tube have inclined portions that are linearly inclined outward in the front-rear direction toward the center portion in the left-right direction of the heat exchange tube. Since the angle between the inclined part and the left and right side edges of the corrugated fin is 25 to 40 degrees, the inclined part of the front and rear end walls of the heat exchange pipe and the left and right side edges of the corrugated fin In the meantime, a corner portion having a sharp corner at the inner side in the width direction of the heat exchange tube is formed. Therefore, the condensed water generated on the surface of the corrugated fin flows so as to be attracted to the entering corner portion by surface tension, and then flows downward through the entering corner portion. Therefore, the drainage of the condensed water generated on the surface of the corrugated fin 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.

  According to the evaporator of the above 2), without disturbing the flow of condensed water into the corners formed between the inclined portions of the front and rear end walls of the heat exchange pipe and the left and right side edges of the corrugated fin, A decrease in heat transfer performance due to a decrease in the contact area between the heat exchange pipe and the corrugated fin can be suppressed.

  According to the evaporator of 5) above, on the left and right side portions of the front and rear end walls of the heat exchange tube, it is relatively easy to incline in a straight line outward in the front-rear direction toward the center in the left-right direction of the heat exchange tube. The angle formed between the inclined portion and the left and right side edges of the corrugated fin can be set to 25 to 40 degrees.

  According to the evaporator of 6), it is possible to prevent the condensed water from scattering from the front edge of the flat hollow body.

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 AA line expanded sectional view of Drawing 1 which omitted some. FIG. 3 is an enlarged sectional view taken along line B-B in FIG. 2. It is a graph which shows the result of Experimental example 1-2 and Comparative experimental example 1-2. In Experimental Examples 1 and 2 and Comparative Experimental Example 1, the length of the contact portion between the left and right side surfaces of the heat exchange pipe and the corrugated fin with respect to the water retention amount at the time when 30 minutes have elapsed and the width in the front and rear direction of the heat exchange pipe It is a graph which shows the relationship between the contact ratio which is a ratio, and the angle which the inclination part of the heat exchange pipe | tube in Experimental Examples 1-2 and Comparative Experimental Example 1 and the right-and-left both sides edge part of a corrugated fin make. The drainage and heat transfer in Experimental Examples 1 and 2 and Comparative Experimental Example 1 obtained from the graph of FIG. 5, and the inclined portions of the heat exchange tubes and the left and right side edges of the corrugated fin in Experimental Examples 1 and 2 and Comparative Experimental Example 1 It is a graph which shows the relationship of the angle which makes. It is a figure equivalent to FIG. 2 which shows the evaporator of Embodiment 2 of this invention. FIG. 8 is an enlarged cross-sectional view taken along the line CC in which a part of FIG. It is a figure equivalent to FIG. 2 which shows Embodiment 3 of the evaporator of this invention. FIG. 10 is an enlarged sectional view taken along the line DD, with a part of FIG.

  Embodiments of the present invention will be described below with reference to the drawings. Throughout the drawings, the same parts and the same parts are denoted by the same reference numerals, and redundant description is omitted.

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

Embodiment 1
This embodiment is shown in FIGS. FIG. 1 shows the overall configuration of the evaporator, and FIGS. 2 and 3 show the configuration of the main part of the evaporator.

  In FIGS. 1 and 2, the evaporator (1) includes an aluminum first header tank (2) and an aluminum second header tank (3) that are spaced apart in the vertical direction and extend in the horizontal direction, and both headers. The tank (2) (3) is spaced in the left-right direction (the length direction of the header tank (2) (3)) with the width direction facing in the front-rear direction and the length direction facing in the up-down direction. A plurality of flat aluminum hollow bodies (4) arranged, a ventilation gap between adjacent flat hollow bodies (4), and a flat hollow body arranged outside the flat hollow bodies (4) at both left and right ends, respectively. Corrugated fins (5) with aluminum louver brazed to (4) and aluminum side plates (6) arranged on the outside of the corrugated fins (5) on both left and right ends and brazed to the corrugated fins (5) ).

  The first header tank (2) is located on the front side (downstream side in the ventilation direction) and extends in the left-right direction, and the refrigerant inlet header portion (7) extends on the rear side (upstream side in the ventilation direction) and extends in the left-right direction. An outlet header portion (8) and a connecting portion (9) for connecting and integrating the header portions (7) and (8) to each other are provided. An aluminum refrigerant inlet pipe (11) is connected to the refrigerant inlet header section (7) of the first header tank (2), and an aluminum refrigerant outlet pipe (12) is connected to the refrigerant outlet header section (8). . The second header tank (3) includes a first intermediate header portion (13) located on the front side and extending in the left-right direction; a second intermediate header portion (14) located on the rear side and extending in the left-right direction; A connecting portion (15) for connecting and integrating the portions (13) and (14) to each other;

  The first header tank (2) is a plate-shaped first member (16) formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides and connected to all flat hollow bodies (4). A second member (17) formed by pressing an aluminum brazing sheet having a brazing material layer on both sides and covering the upper side of the first member (16); and an aluminum brazing sheet having a brazing material layer on both sides Alternatively, a flat partition formed by pressing aluminum bare material and disposed between the first member (16) and the second member (17) and brazed to both members (16) and (17). A part forming plate (18) and a first member (16), a second member (17) and a partition part forming plate (18) formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides. ) On both sides The left and right aluminum left and right end members (19) and the outer end of the right end member (19) are made of aluminum which is brazed to straddle the refrigerant inlet header (7) and the refrigerant outlet header (8) in the front-rear direction. The refrigerant inlet pipe (11) and the refrigerant outlet pipe (12) are connected to the joint plate (21). The joint plate (21) is formed by pressing an aluminum bear material.

  The first member (16) includes a front and rear header forming portions (22) and (23) having a downward bulging shape that form lower portions of the refrigerant inlet header portion (7) and the refrigerant outlet header portion (8), and front and rear header formation. The portions (22) and (23) are integrally connected to each other and are formed with a connecting wall (24) that forms the lower portion of the connecting portion (9). A plurality of pipe insertion holes (25) that are long in the front-rear direction in the header forming portions (22), (23) of the first member (21) are spaced in the left-right direction and are located at the same position in the left-right direction. Is formed.

  The second member (17) includes upper and lower front and rear header forming portions (26) and (27) forming upper portions of the refrigerant inlet header portion (7) and the refrigerant outlet header portion (8), and front and rear header formation. The portions (26) and (27) are integrally connected to each other and the connecting wall (28) forming the upper portion of the connecting portion (9).

  The partition forming plate (18) includes a front partition (29) that divides the refrigerant inlet header (7) into two upper and lower spaces (7A) and (7B), and a refrigerant outlet header (8). The rear partition section (31) partitioned into two spaces (8A) and (8B) and the partition sections (29) and (31) are integrally connected to form an intermediate portion in the vertical direction of the connection section (9). It consists of a connecting wall (32). On the left side of the flat hollow body (4) disposed at the left end of the front partition (29) of the partition forming plate (18), there are two upper and lower spaces in the refrigerant inlet header (7) ( A communication hole (33) is formed through 7A) and (7B). A plurality of circular communication holes (34) passed through the upper and lower spaces (7A) and (7B) of the refrigerant inlet header (7) in the middle part in the front-rear direction of the front partition (29) of the partition forming plate (18) ) Are formed at intervals in the left-right direction. Further, in the portion excluding the left and right end portions of the rear portion of the rear partition portion (31) of the partition portion forming plate (18), the upper and lower spaces of the refrigerant outlet header portion (8) are long in the left-right direction ( A plurality of oval communication holes (35) through which 8A and 8B are passed are formed at intervals in the left-right direction. The length of the oval communication hole (35) in the center is shorter than the lengths of the other oval communication holes (35).

  The left end member (19) closes the left end opening of the refrigerant inlet header portion (7) and the refrigerant outlet header portion (8), and the right end member (19) is the refrigerant inlet header portion (7) and the refrigerant outlet header portion (8 ) Close the right end opening. Although not shown, a refrigerant inlet is formed in a portion facing the upper space (7A) in a portion closing the right end opening of the refrigerant inlet header portion (7) of the right end member (19), and the refrigerant outlet header portion (8) A refrigerant outlet is formed in a portion facing the upper space (8A) in the portion closing the right end opening. The joint plate (21) has a refrigerant passage communicating with the refrigerant inlet and the refrigerant outlet of the right end member (19).

  The second header tank (3) has substantially the same configuration as the first header tank, and is disposed upside down with respect to the first header tank (2). .

  The header forming portions (22) and (23) of the first member (16) of the second header tank (3) form the upper portions of the first intermediate header portion (13) and the second intermediate header portion (14). The header forming portions (26) and (27) of the second member (17) form the lower portions of the first intermediate header portion (13) and the second intermediate header portion (14). The first intermediate header portion (13) is divided into two upper and lower spaces (13A) and (13B) by the front partition portion (29) of the partition portion forming plate (18), and the rear partition portion (31). The inside of the second intermediate header portion (14) is partitioned into two upper and lower spaces (14A) and (14B). Furthermore, the intermediate part of the connection part (15) in the up-down direction is formed by the connection wall (32) of the partition part forming plate (18).

  The difference between the second header tank (3) and the first header tank (2) is as follows.

  The first difference is that the first intermediate header portion (13) is separated from the lower space (13B) (14B) between the intermediate header portions (13) and (14) of the second member (17). A plurality of communication portions (36) for allowing passage through the lower space (13B) and the lower space (14B) of the second intermediate header portion (14) are provided at intervals in the left-right direction. is there. The communicating portion (36) is a flat hollow body (4) adjacent in the left-right direction at a plurality of locations in the second intermediate header portion (14) where the amount of refrigerant in the length direction of the second header tank (3) can be made uniform. ) It is provided between each other.

  The second difference is that instead of the communication hole (33) and the circular communication hole (34) in the front partition part (29) of the partition part forming plate (18), a plurality of relatively large squares that are long in the left-right direction. Communication holes (37) are formed at intervals in the left-right direction, and a plurality of circular communication holes (38) are provided in the rear portion of the rear partition (31) instead of the oval communication holes (34). That is, it is formed in a penetrating manner with an interval in the left-right direction.

  The third difference is that the refrigerant inlet and the refrigerant outlet are not formed in the right end member (21), and the joint plate (21) is not brazed.

  As shown in FIG. 2 and FIG. 3, the flat hollow body (4) is composed of two rectangular metal plates (41) made of pressed aluminum brazing sheet and the front and rear side edges and the center in the front-rear direction. Two heat exchange pipes (45), which are formed by brazing each other over the entire length and open in the vertical direction and open at both the upper and lower ends, are spaced apart in the front-rear direction, that is, the first header tank. (2) and the number of header portions (7), (8), (13) and (14) of the second header tank (3) are provided. The heat exchange pipe (45) of the flat hollow body (4) is located between the brazed part (46) between the front and rear side edges of both metal plates (41) and the brazed part (47) between the central parts in the front and rear direction. In this portion, both metal plates (41) are provided by forming outward bulging portions (48) extending over the entire length, and are flattened with the width direction in the front-rear direction.

  The upper and lower ends of the brazed portion (46) between the front and rear side edges of both metal plates (41) in the flat hollow body (4) are cut off from the front and rear outer edge to the upper and lower end surfaces. The excised part is indicated by (51). In addition, the upper and lower ends of the brazed portion (47) between the center portions in the front-rear direction of both metal plates (41) in the flat hollow body (4) are wider in the front-rear direction than the other portions, and are wider. A notch (52) is formed in the brazed portion (47a) from the outer end in the vertical direction. In addition, by providing the flat hollow body (4) with the wide brazed portion (47a), the upper and lower end portions of the heat exchange tube (45) are narrower in the front-rear direction than the other portions. Then, the cut portion (51) is formed in the brazed portion (46) at the front and rear side edges, and the notch (52) is formed in the wide brazed portion (47a) in the center portion in the front and rear direction. The upper and lower ends of each heat exchange pipe (45) protrude outward in the vertical direction from the other parts, and the protrusions are pipes of the first header tank (2) and the second header tank (3). The insertion portion (53) is inserted into the insertion hole (25). In the flat hollow body (4), the upper and lower end insertion portions (53) of the front heat exchange pipe (45) are arranged on the front side of the first member (16) in the first header tank (2) and the second header tank (3). Inserted into the pipe insertion hole (25) and the upper and lower end insertion portions (53) of the rear heat exchange pipe (45) are the first members in the first header tank (2) and the second header tank (3). (16) The bottom portion of the cut portion (51) of the brazed portion (46) of the front and rear side edges of the flat hollow body (4) and the center portion in the front-rear direction are inserted into the rear tube insertion hole (25). The bottom side of the notch (52) of the wide brazed portion (47a) of the first header tank (2) and the second header tank (3) are the header forming portions (22) and (23) of the first member (16). ) In a state where the end of the flat hollow body (4) is positioned by contacting the outer surface, it is brazed to the first member (16) of both header tanks (2) (3). The corrugated fin (5) is shared by both the front and rear heat exchange tubes (45) of the flat hollow body (4), and the corrugated fin (5) has a wave crest or wave bottom brazed to the heat exchange tube (45). Has been. A plurality of louvers are formed at the connecting portion between the wave crest and the wave bottom of the corrugated fin (5). Further, an aluminum corrugated inner fin (54) is disposed so as to straddle both heat exchange tubes (45) of the flat hollow body (4), and is brazed to both metal plates (41).

  The left and right sides of both front and rear end walls (45a) of both heat exchange pipes (45) of the flat hollow body (4) are linearly outward in the front-rear direction toward the center in the left-right direction of the heat exchange pipe (45). An inclined portion (55) is provided. That is, the front and rear side walls (48a) of the outwardly bulging portion (48) forming both heat exchange tubes (45) in each metal plate (41) of the flat hollow body (4) are formed on the flat hollow body (4). It inclines linearly outward in the front-rear direction toward the center of the thickness. In addition, there are entry corner portions (56) between the outer surfaces of the inclined portions (55) of the front and rear end walls (45a) of the flat hollow heat exchange pipe (45) and the left and right side edges of the corrugated fin (5), respectively. Is formed. The corner portion on the inner side in the width direction of the heat exchange tube (45) in the entering corner portion (56) is an acute angle. The angle θ formed between the inclined portion (55) of the front and rear end walls (45a) of both heat exchange tubes (45) and the left and right side edges of the corrugated fin (5) is determined by the flat hollow body (4) and the corrugated fin (5). Considering the drainage properties of the condensed water generated on the surface, the angle is 25 to 40 degrees. In addition, when the width of the heat exchange pipe (45) in the front-rear direction is W1mm and the length of the contact part between the left and right sides of the heat exchange pipe (45) and the corrugated fin (5) is W2mm, heat exchange The width of the pipe (45) in the front-rear direction: W1 is the ratio of the length in the front-rear direction of the contact portion between the left and right side surfaces of the heat exchange pipe (45) and the corrugated fin (5): W2 / W1 = 80 to 95% is preferable. Furthermore, the width W1 in the front-rear direction of the heat exchange tube (45) is preferably 10 to 20 mm, and the thickness H in the left-right direction of the heat exchange tube (45) is preferably 1 to 1.8 mm.

  At the front and rear side edges of the flat hollow body (4), the metal plate (41) of either of the two metal plates (41) has a tip portion of the other metal plate than the other metal plate (41). A protrusion (57) protruding toward the corrugated fin (5) with which the plate (41) is in contact is formed over the entire length. That is, on the front edge of the left metal plate (41) of the flat hollow body (4), a protrusion (57) whose tip protrudes to the right of the right metal plate (41) is formed over the entire length, and also on the right side. On the rear edge of the metal plate (41), a protrusion (57) is formed over the entire length with the tip protruding leftward from the left metal plate (41).

  The above-described evaporator (1) is manufactured by combining all parts except the inlet pipe (11) and the outlet pipe (12) and brazing them together.

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

  In the above-described evaporator (1), when the compressor is turned on, the gas-liquid mixed phase two-phase refrigerant that has passed through the compressor, the condenser, and the expansion valve passes from the refrigerant inlet pipe (11) to the upper space of the refrigerant inlet header (7) ( 7A), the lower space (7B), the heat exchange pipe (45) on the front side of the flat hollow body (4), the upper space (13A) of the first intermediate header (13), the lower space ( 13B), lower space (14B) of the second intermediate header (14), heat exchange pipe (45) on the rear side of the flat hollow body (4), lower space (8B) of the refrigerant outlet header (8) Then, it flows out to the refrigerant outlet pipe (12) through the upper space (8A).

  Then, while the refrigerant flows in both the front and rear heat exchange pipes (45) of the flat hollow body (4), the refrigerant exchanges heat with the air passing through the ventilation gap between the adjacent flat hollow bodies (4). Flows out in the gas phase.

  At this time, condensed water is generated on the surface of the corrugated fin (5). This condensed water is caused by the surface tension between the outer surface of the inclined portion (55) of the front and rear end walls (45a) of the heat exchange pipe (45) in the flat hollow body (4) and the left and right side edges of the corrugated fin (5). It flows so as to be attracted to the entering corner portion (56) formed at the bottom, and then flows downward through the entering corner portion (56). Accordingly, the drainage of the condensed water is improved, and the performance of the evaporator (1) is prevented from being lowered. Further, the forward scattering of the condensed water is suppressed by the action of the protrusions (57) on the front side edge of the flat hollow body (4).

  Next, an experimental example using the flat hollow body (4) of the evaporator (1) of Embodiment 1 will be described together with a comparative experimental example.

Experimental example 1
Flat hollow body (4), corrugated fin (5), and side plate excluding both header tanks (2) and (3), refrigerant inlet pipe (11) and refrigerant outlet pipe (12) from evaporator (1) of Embodiment 1 A brazed combination of (6) was prepared. The angle θ formed by the inclined portions (55) of the front and rear end walls (45a) of the heat exchange pipe (45) of the flat hollow body (4) and the left and right side edges of the corrugated fin (5) is 25 degrees. Then, the combination was immersed in water in the water tank, and the air remaining in the combination was removed, and then left for 30 minutes. Next, the combination was lifted so that the flat hollow body (4) was vertical and taken out of the water, and in this state, the weight of the combination was measured for 30 minutes to examine the change in the water retention amount.

Experimental example 2
The same combination as in Experimental Example 1 except that the angle θ between the inclined portion (55) of the front and rear end walls (45a) of the heat exchange pipe (45) and the left and right side edges of the corrugated fin (5) is 35 degrees. A body was prepared, and the change in water retention amount was examined in the same manner as in Experimental Example 1. The width W1 in the front-rear direction of the heat exchange tube (45) and the thickness H in the left-right direction of the heat exchange tube (4) are the same as those in Experimental Example 1.

Comparative Experiment Example 1
The same combination as in Experimental Example 1 except that the angle θ between the inclined part (55) of the front and rear end walls (45a) of the heat exchange pipe (45) and the left and right side edges of the corrugated fin (5) is 45 degrees. A body was prepared, and the change in water retention amount was examined in the same manner as in Experimental Example 1. The width W1 in the front-rear direction of the heat exchange tube (45) and the thickness H in the left-right direction of the heat exchange tube (4) are the same as those in Experimental Example 1.

Comparative Experiment Example 2
Instead of a flat hollow body (4), a combination of two heat exchange tubes lined up in the front-rear direction, a corrugated fin (5), and a side plate (6) brazed did. As the heat exchange tube, a heat exchange tube described in Patent Document 1, that is, a heat exchange tube in which the cross-sectional shape of the front and rear end walls is an arc shape protruding outward in the front-rear direction is used. Note that the width in the front-rear direction and the thickness in the left-right direction of the heat exchange tube of Comparative Experimental Example 2 are the same as those of Experimental Example 1. And the water retention amount change was investigated like Experimental example 1. FIG.

  The results of Experimental Examples 1-2 and Comparative Experimental Examples 1-2 are shown in FIG. As is clear from the results shown in FIG. 4, in Experimental Examples 1 and 2, the amount of water retained after 30 minutes has decreased compared to Comparative Experimental Examples 1 and 2, and the drainage is excellent. I understand.

  Moreover, the water retention amount of Experimental Examples 1 and 2 and Comparative Experimental Example 1, the width in the front-rear direction of the heat exchange pipes of Experimental Examples 1 and 2 and Comparative Experimental Example 1, and the left and right side surfaces of the heat exchange pipe with respect to W1 and the corrugated fins The relationship between the length of the contact portion in the front-rear direction: W2 and the contact ratio: W2 / W1, and the angle between the inclined portions of the front and rear end walls of the heat exchange tube and the left and right side edges of the corrugated fins are shown in FIG. As shown in FIG.

  Further, FIG. 6 shows the relationship between the contact ratio: the ratio of the water retention amount to W2 / W1 and the angle: θ between the inclined portions of the front and rear end walls of the heat exchange pipe and the left and right side edges of the corrugated fin. The above contact ratio: the smaller the ratio of the water retention amount to W2 / W1, the lowering of the drainage is prevented, and the reduction of the heat transfer performance due to the reduction of the contact area between the heat exchange pipe and the corrugated fin is suppressed. It means that it is possible. Therefore, from the results shown in FIG. 6, when the angle between the inclined portions of the front and rear end walls of the heat exchange pipe and the left and right side edges of the corrugated fin: θ is 25 to 40 degrees, the necessary heat transfer properties are secured. Thus, it is possible to improve drainage of condensed water.

Embodiment 2
This embodiment is shown in FIG. 7 and FIG. 7 and 8 show the configuration of the main part of the evaporator.

  7 and 8, the evaporator (60) includes an aluminum first header tank (61) and an aluminum second header tank (62) which are arranged at intervals in the vertical direction and extend in the horizontal direction, and both headers. Between the tanks (61) and (62), the plurality of flat aluminum hollow bodies (63) and the adjacent flat hollow bodies (63) disposed between the tanks (61) and (62) with the width direction directed in the front-rear direction and spaced in the left-right direction. Between the corrugated fins (5), and the aluminum corrugated fins (5) disposed on the outside of the flat hollow bodies (63) on both the left and right ends and brazed to the flat hollow bodies (63), respectively And aluminum side plates (not shown) brazed to the corrugated fins (5).

  The whole of the first header tank (61) is a refrigerant inlet header part (65), and the whole of the second header tank (62) is a refrigerant outlet header part (66). A refrigerant inlet pipe (not shown) is connected to the refrigerant inlet header part (65) of the first header tank (61), and an aluminum refrigerant outlet pipe (not shown) is connected to the refrigerant outlet header part (66) of the second header tank (62). Abbreviation) is connected.

  The first header tank (61) is formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides, and a plate-shaped first member (67) to which all flat hollow bodies (63) are connected. A second member (68) formed by pressing an aluminum brazing sheet having a brazing material layer on both sides and covering the upper side of the first member (67); and an aluminum brazing sheet having a brazing material layer on both sides Alternatively, a flat partition formed by pressing an aluminum bare material and disposed between the first member (67) and the second member (68) and brazed to both members (67) (68). A part forming plate (69) and a first member (67), a second member (68) and a partition part forming plate (69) formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides. ) On both sides And left and right aluminum left and right end members (not shown).

  The first member (67) forms the lower part of the refrigerant inlet header part (65), and the second member (68) forms the upper part of the refrigerant inlet header part (65). A plurality of pipe insertion holes (71) that are long in the front-rear direction are formed in the first member (67) at intervals in the left-right direction. The partition forming plate (69) includes a partition (73) that partitions the refrigerant inlet header (65) into two upper and lower spaces (65A) and (65B). A plurality of relatively large rectangular communication holes (74) that are long in the left-right direction are formed at intervals in the left-right direction on the front and rear portions of the partition (73) of the partition forming plate (69). Has been. The left and right end members close the left and right end openings of the refrigerant inlet header portion (65). A refrigerant inlet is formed in a portion corresponding to the upper space (65A) in the left end member or the right end member.

  The second header tank (62) has the same configuration as the first header tank (61) and is disposed upside down with respect to the first header tank (61). .

  The first member (67) of the second header tank (3) forms the upper part of the refrigerant outlet header part (66), and the second member (68) forms the lower part of the refrigerant outlet header part (66). Further, the inside of the refrigerant outlet header portion (66) is partitioned into two upper and lower spaces (66A) and (66B) by the partition portion (73) of the partition portion forming plate (69). Further, a refrigerant outlet is formed in a portion corresponding to the lower space (66B) in the left end member or the right end member.

  The flat hollow body (63) is formed by brazing the front and rear side edges of two rectangular metal plates (75) made of pressed aluminum brazing sheet over the entire length. The number of heat exchange pipes (76) extending in the vertical direction and having both upper and lower ends opened is the same as the number of header portions (65) and (66) of the first header tank (61) and the second header tank (62), that is, 1 Only one is provided. The heat exchange pipe (76) of the flat hollow body (63) is connected to the two metal plates (75) over the entire length in the portion between the brazed portions (77) between the front and rear side edges of the two metal plates (75). It is provided by forming the side bulging portion (78), and has a flat shape with the width direction directed in the front-rear direction.

  The upper and lower ends of the brazed portion (77) between the front and rear side edges of both metal plates (75) in the flat hollow body (63) are cut away from the front and rear direction outer edge to the upper and lower end surfaces. The excised part is indicated by (81). Then, by forming the cut portions (81) in the brazed portions (77) on the front and rear side edges, the upper and lower ends of each heat exchange tube (76) protrude outward in the vertical direction from the other portions. Thus, the projecting portion is an insertion portion (82) that is inserted into the pipe insertion hole (71) of the first header tank (61) and the second header tank (63). In the flat hollow body (63), the upper and lower end insertion portions (82) of the heat exchange pipe (76) are inserted into the pipe insertion holes of the first member (67) in the first header tank (61) and the second header tank (62). (71), and the bottom part of the cut part (81) of the brazed part (77) at the front and rear side edges of the flat hollow body (63) is the first header tank (61) and the second header tank (62 ) In the state where the end of the flat hollow body (63) is positioned by contacting the outer surface of the first member (67) in the first member (67) of both header tanks (61) and (62). It is brazed. The corrugated fin (5) is brazed to the heat exchange pipe (76) at the wave crest or wave crest. An aluminum corrugated inner fin (79) is disposed in the heat exchange pipe (76) of the flat hollow body (63), and is brazed to both metal plates (75).

  The left and right sides of the front and rear end walls (76a) of the heat exchange pipe (76) of the flat hollow body (63) are linearly outward in the front-rear direction toward the center in the left-right direction of the heat exchange pipe (76). An inclined portion (83) that is inclined is provided. That is, the front and rear side walls (78a) of the outwardly bulging portion (78) forming both heat exchange tubes (76) in each metal plate (75) of the flat hollow body (63) are the flat hollow body (63). It inclines linearly outward in the front-rear direction toward the center of the thickness. And, between the inclined surface (83) outer surface of the front and rear end walls (75a) of the heat exchange tube (76) in the flat hollow body (63) and the left and right side edges of the corrugated fin (5), 84) is formed. The corner portion on the inner side in the front-rear direction of the entering corner portion (84) is an acute angle. The angle θ between the inclined part (83) of the front and rear end walls (76a) of the heat exchange pipe (76) and the left and right side edges of the corrugated fin (5) is determined by the flat hollow body (63) and the corrugated fin (5). Considering the drainage of the condensed water generated on the surface, it is 25 to 40 degrees. In addition, when the width in the front-rear direction of the heat exchange pipe (76) is W1 mm and the length in the front-rear direction of the contact portion between the left and right side surfaces of the heat exchange pipe (76) and the corrugated fin (5) is W2 mm, heat exchange Width in the front-rear direction of the tube (76): The length in the front-rear direction of the contact portion between the left and right side surfaces of the heat exchange tube (76) and the corrugated fin (5) with respect to W1: Contact ratio that is a ratio of W2: W2 / W1 = 80 to 95% is preferable. Furthermore, the width W1 in the front-rear direction of the heat exchange tube (76) is preferably 10 to 20 mm, and the thickness H in the left-right direction of the heat exchange tube (76) is preferably 1 to 1.8 mm.

  At the front and rear side edges of the flat hollow body (63), one of the two metal plates (75) is attached to one of the metal plates (75), and the other end of the metal plate (75) is more distal than the other metal plate (75). A protrusion (85) protruding toward the corrugated fin (5) with which the plate (75) is in contact is formed over the entire length. That is, on the front edge of the left metal plate (75) of the flat hollow body (63), a protrusion (85) whose tip protrudes rightward from the right metal plate (75) is formed over the entire length, and also on the right side. On the rear edge of the metal plate (75), a ridge (85) having a tip protruding leftward from the left metal plate (75) is formed over the entire length.

  The evaporator (60) constitutes a refrigeration cycle using a chlorofluorocarbon refrigerant together with a compressor and a condenser as a refrigerant cooler, and is mounted on a vehicle such as an automobile as a car air conditioner.

  In the above-described evaporator (60), when the compressor is turned on, the gas-liquid mixed phase two-phase refrigerant that has passed through the compressor, the condenser, and the expansion valve passes through the refrigerant inlet of the right end member or the left end member from the refrigerant inlet pipe to the first header. The refrigerant enters the refrigerant inlet header part (65) of the tank (61), and flows out to the refrigerant outlet pipe through the heat exchange pipe (76) and the refrigerant outlet header part (66).

  While the refrigerant flows in the heat exchange pipe (76) of the flat hollow body (63), heat exchange is performed with the air passing through the ventilation gap between the adjacent flat hollow bodies (63). It flows out as a phase.

  At this time, condensed water is generated on the surface of the corrugated fin (5). This condensed water is formed between the outer surface of the inclined portion (83) of the front and rear end walls of the heat exchange pipe (76) of the flat hollow body (63) and the left and right side edges of the corrugated fin (5) by surface tension. It flows so as to be attracted to the corner portion (84), and then flows downward through the corner portion (84). Accordingly, the drainage of the condensed water is improved, and the performance of the evaporator (1) is prevented from being lowered. Further, the forward scattering of the condensed water is suppressed by the action of the protrusions (85) at the front edge of the flat hollow body (63).

Embodiment 3
This embodiment is shown in FIG. 9 and FIG. 9 and 10 show the configuration of the main part of the evaporator.

  9 and 10, the evaporator (90) has the same configuration as the two header tanks (2) and (3) of the evaporator (1) of the first embodiment and is arranged at intervals in the vertical direction. 1 header tank (2) and 2nd header tank (3) are provided. Are arranged at intervals in the vertical direction. Between the header tanks (2) and (3), the header portions (7) and (8) of both header tanks (2) and (3) are arranged with the width direction facing in the front-rear direction and spaced in the front-rear direction. 13) As many as (14), here a set of two flat extruded heat exchanger tubes (91) made of aluminum extrusions (91) are arranged in the left and right direction at intervals, and both front and rear heat exchange tubes ( 91) Aluminum corrugated fins (5) are arranged on the outside of the pair (92) at the left and right ends, and the corrugated fins (5) are brazed to the heat exchange pipe (91), and left and right Aluminum side plates (not shown) are respectively disposed outside the corrugated fins (5) at both ends and brazed to the corrugated fins (5).

  With the upper and lower ends of the front heat exchange pipe (91) inserted into the front pipe insertion holes (25) of the first member (16) in the first header tank (2) and the second header tank (3) The upper and lower end portions of the rear heat exchange pipe (91) are brazed to the first member (16) of both header tanks (2) and (3), and the first header tank (2) and the second header tank ( In the state of being inserted into the rear pipe insertion hole (25) of the first member (16) in 3), it is brazed to the first member (16) of both header tanks (2) and (3). The corrugated fin (5) is shared by both the front and rear heat exchange pipes (91), and the wave top or wave bottom of the corrugated fin (5) is brazed to the heat exchange pipe (91).

  The left and right side portions of the front and rear end walls (91a) of the heat exchange pipe (91) are inclined portions (93) that are inclined linearly outward in the front-rear direction toward the center in the left-right direction of the heat exchange pipe (91). Is provided. In the portion between both inclined portions (93) in the front and rear end walls (91a), there are portions perpendicular to the left and right side edges of the corrugated fin (5). In addition, corner portions (94) are formed between the outer surface of the inclined portion (93) of the front and rear end walls (91a) of the heat exchange pipe (91) and the left and right side edges of the corrugated fin (5), respectively. . The corner portion on the inner side in the width direction of the heat exchange pipe (91) in the entering corner portion (94) is an acute angle. The angle θ formed by the inclined portions (93) of the front and rear end walls (91a) of the heat exchange pipe (91) and the left and right edges of the corrugated fin (5) is determined between the heat exchange pipe (91) and the corrugated fin (5). Considering the drainage of the condensed water generated on the surface, it is 25 to 40 degrees. In addition, when the width in the front-rear direction of the heat exchange pipe (91) is W1 mm and the length in the front-rear direction of the contact portion between the left and right side surfaces of the heat exchange pipe (91) and the corrugated fin (5) is W2 mm, heat exchange The width in the front-rear direction of the pipe (91): W1 is the ratio of the length in the front-rear direction of the contact portion between the left and right side surfaces of the heat exchange pipe (91) and the corrugated fin (5): W2 / W1 = 80 to 95% is preferable. Furthermore, the width W1 in the front-rear direction of the heat exchange tube (91) is preferably 10 to 20 mm, and the thickness T in the left-right direction of the heat exchange tube (91) is preferably 1 to 1.8 mm.

  The evaporator (90) constitutes a refrigeration cycle using a chlorofluorocarbon refrigerant together with a compressor and a condenser serving as a refrigerant cooler, and is mounted on a vehicle such as an automobile as a car air conditioner.

  In the evaporator (90) described above, when the compressor is turned on, the gas-liquid mixed phase two-phase refrigerant that has passed through the compressor, the condenser, and the expansion valve flows from the refrigerant inlet pipe (11) to the upper space of the refrigerant inlet header (7) ( 7A), the lower space (7B), the front heat exchange pipe (91), the upper space (13A) of the first intermediate header (13), the lower space (13B), the second intermediate header The refrigerant outlet pipe (12B) passes through the lower space (14B) of the section (14), the rear heat exchange pipe (91), the lower space (8B) and the upper space (8A) of the refrigerant outlet header section (8). ).

  While the refrigerant flows in both the front and rear heat exchange pipes (91), heat exchange is performed with the air passing through the ventilation gap between the sets (92) of adjacent heat exchange pipes (91). It flows out in the gas phase.

  At this time, condensed water is generated on the surface of the corrugated fin (5). This condensed water is formed by the surface tension between the outer surfaces of the inclined portions (93) of the front and rear end walls (91a) of each heat exchange pipe (91) and the left and right side edges of the corrugated fin (5). It flows so as to be attracted to the part (94) and then flows downward through the corner part (94). Accordingly, the drainage of the condensed water is improved, and the performance of the evaporator (1) is prevented from being lowered.

  The evaporator according to the present invention is suitably used for a refrigeration cycle constituting a car air conditioner.

(1) (60) (90): Evaporator
(2) (3) (61) (62): Header tank
(4) (63): Flat hollow body
(5): Corrugated fin
(41) (75): Metal plate
(48) (78): Outward bulge
(48a) (78a): Both front and rear walls
(45) (76) (91): Heat exchange tube
(45a) (76a) (91a): Front and rear end walls
(55) (83) (93): Inclined part
(57) (85): Projection

Claims (6)

Between a pair of header tanks arranged at intervals in the vertical direction and between the two header tanks, the width direction is directed in the front-rear direction and is arranged at intervals in the left-right direction, and both ends are connected to the header tank. An evaporator comprising a plurality of flat heat exchange tubes and corrugated fins arranged between adjacent heat exchange tubes,
The left and right side portions of the front and rear end walls of the heat exchange tube are provided with inclined portions that are linearly inclined outwardly in the front-rear direction toward the central portion in the left-right direction of the heat exchange tube. An evaporator having an angle of 25 to 40 degrees with the left and right side edges. Corrugated fins are in contact with the left and right side surfaces of the heat exchange pipe, the width in the front-rear direction of the heat exchange pipe is W1 mm, and the length in the front-rear direction of the contact portion between the left and right side surfaces of the heat exchange pipe and the corrugated fin is The evaporator according to claim 1, wherein W2 / W1 = 80 to 95%. The evaporator according to claim 1 or 2, wherein the width of the heat exchange pipe in the front-rear direction is 10 to 20 mm. The evaporator according to any one of claims 1 to 3, wherein a thickness of the heat exchange pipe in the left-right direction is 1 to 1.8 mm. The heat exchange tube is provided in a flat hollow body in which two rectangular metal plates that have been pressed are joined together in a laminated manner, and both metal plates that form the flat hollow body bulge outward The heat exchange pipe with both upper and lower ends opened by being made, and both the front and rear walls of the outward bulge part forming the heat exchange pipe in each metal plate are in the front-rear direction toward the center part of the thickness of the flat hollow body The evaporator according to claim 1, wherein the evaporator is inclined linearly outward. At the front side edge of the flat hollow body, either one of the two metal plates is protruded toward the corrugated fin side where the tip of the metal plate is in contact with the other metal plate rather than the other metal plate. The evaporator according to claim 5, wherein the strip is formed over the entire length.

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