JP2009113625A - Evaporator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an evaporator capable of enhancing water-discharge performance of condensation water from a lower header tank. <P>SOLUTION: The evaporator 30 is provided with a pair of header tanks 31, 32 long in a left/right direction arranged with a gap in a vertical direction; a plurality of heat exchange pipes 33 arranged between both header tanks 31, 32 with a gap in left/right direction; and a fin 34 arranged between the heat exchange pipes 33 adjacent in the left/right direction. The lower header tank 32 is formed by a tank body 36; and a pipe connection plate 37 having an upper surface covering part 38 covering an upper surface of the tank body 36. A water-discharge promotion projection part 59 extending in a longitudinal direction and upwardly projected is provided between the heat exchange pipes 33 adjacent in the left/right direction on an outer surface of the upper surface covering part 38 of the pipe connection plate 37. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

The present invention relates to an evaporator, and more particularly, relates to an evaporator that uses a supercritical refrigerant such as CO ₂ (carbon dioxide) and is preferably used as an evaporator of a supercritical refrigeration cycle mounted on a vehicle as a car air conditioner. .

  In this specification and claims, the term “supercritical refrigeration cycle” means a refrigeration cycle in which the refrigerant is in a supercritical state exceeding the critical pressure on the high pressure side, and “supercritical refrigerant” It shall mean a refrigerant used in a supercritical refrigeration cycle.

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

  For example, as an evaporator of a supercritical refrigeration cycle applied to a car air conditioner for a vehicle, conventionally, a pair of header tanks that are arranged in the vertical direction and spaced in the horizontal direction, and a gap in the horizontal direction between the header tanks. A plurality of heat exchange tubes arranged in a row and spaced apart in the front-rear direction, and corrugated fins arranged between the heat exchange tubes adjacent in the left-right direction. What you have is known.

  However, in this evaporator, a relatively large amount of condensed water accumulates between the upper surface of the lower header tank and the lower end of the corrugated fin, and the air-side pressure loss increases to deteriorate the performance of the evaporator, or the condensed water is scattered. There is a risk.

  Therefore, as an evaporator that solves such a problem, a pair of header tanks that are long in the left-right direction and spaced apart in the vertical direction, and a plurality of header tanks that are spaced in the left-right direction between both header tanks A lower header tank comprising two rows of heat exchange tubes that are formed of heat exchange tubes and spaced in the front-rear direction, and corrugated fins disposed between the heat exchange tubes adjacent in the left-right direction. However, the outer plate and the inner plate are laminated and brazed, and the outer plate has an outward bulging portion that extends in the left-right direction and whose opening is closed by the inner plate. An upper bulging portion extending in the front-rear direction to a portion corresponding to each heat exchange pipe in the inner plate is formed with two refrigerant circulation portions communicating with the passage of the exchange pipe spaced apart in the front-rear direction The end of the heat exchange tube is inserted into the tube insertion hole formed in the upper bulging portion and brazed to the inner plate, and the portion between the adjacent upper bulging portions at the front and rear side edges of the lower header tank An evaporator having a drainage groove formed therein is known (see Patent Document 1).

However, in the case of the evaporator described in Patent Document 1, an upper bulging portion is formed in a portion corresponding to each heat exchange tube in the inner plate, and an end portion of the heat exchange tube is inserted into a tube insertion hole formed in the upper bulge portion. Since it is inserted and brazed to the inner plate, the joint area between the inner plate and the outer plate becomes relatively small, and the pressure resistance of the lower header tank may be reduced. In particular, when used in an evaporator of a supercritical refrigeration cycle, pressure resistance is insufficient.
JP-A-2005-283018

  An object of the present invention is to provide an evaporator that can solve the above-described problems and improve the drainage performance of condensed water from the lower header tank.

  In order to achieve the above object, the present invention comprises the following aspects.

1) A pair of header tanks that are arranged in the left-right direction and spaced apart in the vertical direction, and a plurality of heat exchange tubes that are arranged in the left-right direction between the two header tanks are adjacent to each other in the left-right direction. An evaporator comprising a fin body disposed between heat exchange pipes, wherein the lower header tank includes a tank main body and a pipe connecting plate having an upper surface covering portion covering the upper surface of the tank main body,
An evaporator in which a drainage promotion convex portion extending in the front-rear direction and projecting upward is provided between the heat exchange tubes adjacent in the left-right direction on the outer surface of the upper surface covering portion of the pipe connection plate.

  2) A plurality of heat exchange tube groups consisting of a plurality of heat exchange tubes arranged at intervals in the left-right direction are provided at intervals in the front-rear direction, and adjacent to the left-right direction of the heat exchange tube group at the front end. The evaporator according to 1) above, wherein a drainage promotion convex portion is provided between the matching heat exchange tubes.

  3) A plurality of heat exchange tube groups composed of a plurality of heat exchange tubes arranged at intervals in the left-right direction are provided at intervals in the front-rear direction, and heat adjacent to each other in the left-right direction of each heat exchange tube group. The evaporator according to 1) above, wherein a drainage promotion convex portion is provided between the exchange pipes.

  4) The evaporator according to any one of 1) to 3) above, wherein the drainage promotion convex portion is formed by causing the pipe connection plate to bulge upward.

  5) The evaporator according to any one of 1) to 4) above, wherein a drainage groove extending in the vertical direction is formed in a portion corresponding to each heat exchange pipe on the front side surface of the lower header tank.

  6) The evaporator according to 5) above, wherein a drainage auxiliary groove is formed on the upper surface of the lower header tank so as to continue to the upper end of the drainage groove and extend toward the heat exchange pipe.

  7) The pipe connection plate of the lower header tank is connected to the front and rear side edges of the top cover part and has side cover parts covering the front and rear side faces of the tank body, and drainage grooves are formed on the side cover parts. And the evaporator according to 6) above, wherein a drainage auxiliary groove is formed in the upper surface covering portion.

  8) The tank body of the lower header tank has an outer bulge of the first plate between the first plate having at least one outward bulging portion extending in the left-right direction, and the pipe connecting plate and the first plate. A plurality of tube insertion holes in the portion corresponding to the outward bulging portion of the pipe connection plate, the second plate being interposed so as to block the opening of the portion and joined to both plates. A through hole is formed in the second plate of the tank body so that each tube insertion hole of the tube connection plate is led into the outward bulging portion of the first plate. 1) to 7), wherein both ends of the heat exchange pipe are inserted into the pipe insertion holes of the pipe connection plates of both header tanks and brazed to the pipe connection plate. The evaporator.

  According to the evaporators of the above 1) and 2), the drainage promotion convex portion extending in the front-rear direction and projecting upward is provided between the heat exchange tubes adjacent in the left-right direction on the outer surface of the upper surface covering portion of the pipe connection plate. Therefore, when a small amount of condensed water accumulates between the heat exchange pipe and the drainage promotion convex portion, the condensed water is pushed forward by the wind and flows down below the lower header tank. Therefore, the drainage performance of the condensed water from the lower header tank is improved, and a large amount of condensed water is prevented from accumulating between the upper surface of the lower header tank and the lower end of the corrugated fin. As a result, the drainage performance of the condensed water from the lower header tank is improved, and the evaporator has an increased air-side pressure loss due to the accumulation of a large amount of condensed water between the upper surface of the lower header tank and the lower end of the corrugated fin. Performance degradation and splash of condensed water are prevented.

  According to the evaporator 3) above, the drainage performance of the condensed water from the lower header tank is further improved. Further, the amount of wind passing between the upper surface of the lower header tank and the fins is reduced, and the condensate is prevented from scattering.

  Even if the drainage promotion convex part is formed by causing the pipe connection plate to bulge upward like the evaporator in 4) above, the drainage promotion convex part is located between the heat exchange pipes adjacent to the left and right. Therefore, the joint area between the pipe connection plate and the tank body is larger than the joint area between the inner plate and the outer plate in the evaporator described in Patent Document 1, and the pressure resistance of the lower header tank is reduced. Can be prevented.

  According to the evaporators 5) and 6), the drainage performance of the condensed water from the lower header tank is further improved.

  Embodiments of the present invention will be described below with reference to the drawings. In this embodiment, the evaporator according to the present invention is applied to an evaporator of a supercritical refrigeration cycle.

  1 and 2 show the overall structure of an evaporator to which the present invention is applied, FIGS. 3 to 9 show the structure of the main part of the evaporator, and FIG. 10 shows the flow of refrigerant in the evaporator of FIG.

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

1 to 4, an evaporator (30) of a supercritical refrigeration cycle using a supercritical refrigerant, for example, CO ₂ , is provided with two header tanks (31) (31) ( 32) and a plurality of flat heat exchange tubes (33) arranged in parallel in the left-right direction between both header tanks (31), (32), and heat exchange tubes adjacent in the left-right direction ( 33) The ventilation gap between the corrugated fins (34) disposed outside the heat exchange pipes (33) at both the left and right ends and brazed to the heat exchange pipes (33), and the corrugated fins (34 ) And an aluminum bear side plate (35) brazed to the corrugated fin (34).

  The upper header tank (31) is formed of an aluminum tank body (36) and a brazing sheet having a brazing filler metal layer on both sides, here an aluminum brazing sheet, and covers the lower surface of the tank body (36). A pipe connection plate (37) brazed to (36). The tank body (36) is formed of a brazing sheet having a brazing filler metal layer on both sides, here an aluminum brazing sheet, and disposed on the upper side (outside), and a metal bare material, here aluminum. Consists of a second plate (36B) made of a bare material and interposed between the first plate (36A) and the pipe connection plate (37) and brazed to both plates (36A) (37) Has been. In the upper header tank (31), a set of two header portions (1), (2) and (3) (4) formed at intervals in the front-rear direction is spaced 2 in the left-right direction. A set is provided (see FIG. 1).

Two outward bulges (39A) (39B) (39C) (39D) extending in the left-right direction on the right and left sides of the first plate (36A) of the tank body (36) of the upper header tank (31) ) Are formed at intervals in the front-rear direction. The bulge height, length, and width of each of the outward bulge portions (39A) to (39D) are equal. Hereinafter, in this embodiment, the outer bulging portion (39A) of the right front portion is the first outer bulging portion, the outer bulging portion (39B) of the right rear portion is the second outer bulging portion, and the left side. The outer bulging portion (39C) in the front portion is referred to as a third outer bulging portion, and the outer bulging portion (39D) in the left rear portion is referred to as a fourth outer bulging portion. The first outer bulge portion (39A) and the second outer bulge portion (39B) form a pair, and the third outer bulge portion (39C) and the fourth outer bulge portion (39D) A pair is formed. The opening of the first plate (36A) facing the lower side of the internal space (39a) (39b) (39c) (39d) of the first to fourth outward bulges (39A) to (39D) is the second plate. It is blocked by (36B). The internal spaces (39a) and (39b) of the first and second outwardly bulging portions (39A) and (39B) are configured to flow CO ₂ in the left-right direction, respectively. The first plate (36A) is formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides.

  The pipe connecting plate (37) is formed integrally with the lower surface covering portion (38) covering the lower surface of the tank body (36) and the front and rear side edges of the lower surface covering portion (38), and the front and rear side surfaces of the tank body are And a side surface covering portion (42) for covering. A plurality of through-tube insertion holes (41) that are long in the front-rear direction are formed at intervals in the left-right direction on both front and rear side portions of the lower surface covering portion (38) of the pipe connection plate (37). A plurality of tube insertion holes (41) formed in the right half of the front side are formed within the left and right range of the first outer bulge portion (39A) of the first plate (36A), and the right side of the rear side The plurality of tube insertion holes (41) formed in the half are formed in the left-right range of the second outward bulging portion (39B), and the plurality of tube insertion holes formed in the left half of the front side (41) is formed within the range in the left-right direction of the third outward bulge portion (39C), and the plurality of tube insertion holes (41) formed in the left half of the rear side are provided with the fourth outward bulge. It is formed within a range in the left-right direction of the protruding portion (39D). In addition, the length of each tube insertion hole (41) is slightly longer than the width in the front-rear direction of each outward bulge portion (39A) to (39D), and both front and rear end portions of the tube insertion hole (41) are It protrudes outward from both front and rear side edges of the side bulging portions (39A) to (39D) (see FIGS. 3 and 4). Further, each side surface covering portion (42) of the pipe connecting plate (37) protrudes upward, the tip reaches the outer surface of the first plate (36A), and the first plate (36A) and the second plate (36B). The first and second plates (36A) and (36B) are brazed to both front and rear side surfaces. A plurality of engaging portions (43) that engage with the outer surface of the first plate (36A) are integrally formed at the protruding end of each side surface covering portion (42) at intervals in the left-right direction. It is brazed to 36A). The pipe connecting plate (37) is formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides.

  The pipe insertion hole (41) of the pipe connection plate (37) is formed in the second plate (36B) of the tank body (36) of the upper header tank (31), and the outward bulge portion (39A) of the first plate (36A). ) To (39D) are formed in the same number of through-holes (44) that communicate with the internal spaces (39a) to (39d) of the tube insertion holes (41). The communication hole (44) is slightly larger than the tube insertion hole (41). The plurality of tube insertion holes (41) formed in the right half of the front side of the pipe connection plate (37) are connected to a plurality of communication holes (in the right half of the front side of the second plate (36B) ( 44) through the inner space (39a) of the first outward bulge portion (39A), and a plurality of tube insertion holes (41) formed in the right half of the rear side are also provided on the second plate (36B) is connected to the inner space (39b) of the second outer bulge portion (39B) through a plurality of communication holes (44) formed in the right half portion on the rear side, The plurality of tube insertion holes (41) formed in the portion are connected to the third outer bulging portion (39C) via the plurality of communication holes (44) formed in the left half of the front side of the second plate (36B). A plurality of tube insertion holes (41) formed in the left half of the rear side are formed in the left half of the rear side of the second plate (36B). It is made to communicate with the internal space (39d) of the fourth outer bulge portion (39D) through the plurality of communication holes (44). There.

  As shown in FIG. 3 and FIG. 5, all the communication holes leading to the internal space (39a) of the first outwardly bulging portion (39A) of the first plate (36A) in the second plate (36B) of the tank body ( 44) and all the communication holes (44) leading to the internal space (39b) of the second outward bulge part (39B) are respectively between the communication holes (44) adjacent in the left-right direction in the second plate (36B). The communication part (46) formed by excising the center part in the front-rear direction is communicated. And the communication part (46) which makes all the communication holes (44) communicated with the internal space (39a) (39b) of the 1st and 2nd outward bulge part (39A) (39B) of a 1st plate (36A) communicate. ), And the central portion in the front-rear direction of the communication hole (44), the internal space of the first and second outwardly bulging portions (39A) and (39B) of the first plate (36A) on the second plate (36B) ( Refrigerant circulation portions (40A) and (40B) are formed which communicate with 39a) and (39b) and through which the refrigerant flows in the left-right direction.

  As shown in FIGS. 4 and 5, each communication hole (44) leading to the internal space (39c) of the third outer bulging portion (39C) of the first plate (36A) in the second plate (36B) and the first plate (36B) 4 Each communicating hole (44) communicating with the internal space (39d) of the outwardly bulging portion (39D) is to cut out a portion between the communicating holes (44) adjacent in the front-rear direction in the second plate (36B). The refrigerant turn communication portion (45) formed by the first and second outer bulge portions (39C) and (39D) of the first plate (36A) is thereby communicated. ) The two communicate with each other. The second plate (36B) is formed by pressing an aluminum bare material.

  As shown in FIGS. 5 and 6, two right protrusions (36a) (36b) (37a) are provided at the right ends of the three plates (36A) (36B) (37) at intervals in the front-rear direction. ) Is formed. The second plate (36B) is formed with a notch (47) that leads from the front ends of the two front and rear outward projections (36b) to the communication hole (44) at the right end. ) At the right end of the refrigerant inlet (40A) on the front side of the second plate (36B) and the refrigerant inlet (39a) leading to the internal space (39a) of the first outward bulge (39A) of the first plate (36A). 48) and the refrigerant outlet (49b) communicating with the internal space (39b) of the refrigerant circulation part (40B) on the rear side of the second plate (36B) and the second outwardly bulging part (39B) of the first plate (36A). ) And are formed. The refrigerant inflow passage (52) and the refrigerant outlet (52) leading to the refrigerant inlet (48) span the two right protrusions (36a) (36b) (37a) of the three plates (36A) (36B) (37). 49) A refrigerant inlet / outlet member (51) having a refrigerant outlet passage (53) leading to 49) is brazed to the upper header tank (31) by a brazing sheet having a brazing filler metal layer on both sides, here an aluminum brazing sheet (57). Yes. The refrigerant inlet / outlet member (51) is made of a metal bare material, here an aluminum bear material.

  The first and second outwardly bulging portions (39A) (39B) of the two plates (36A) (36B) and the pipe connection plate (37) constituting the tank body (36) of the upper header tank (31). ) To form an inlet header portion (1) and an outlet header portion (2), and two plates (36A) (36B) and a tank body (36) of the upper header tank (31), Two intermediate header portions (3) and (4) are formed by portions corresponding to the third and fourth outwardly bulging portions (39A) and (39B) in the pipe connecting plate (37). The internal space (39a) (39b) of the first and second outwardly bulging portions (39A) (39B) of the first plate (36A) of the tank body (36) and the refrigerant circulation portion of the second plate (36B) ( 40A) (40B) and the opening header portion (1) and the outlet header portion (2) hollow portion (1A) (2A) that is opened downward and the opening is blocked by the pipe connection plate (37) Is formed. Further, the internal space (39c) (39d) of the third and fourth outwardly bulging portions (39C) (39D) of the first plate (36A) of the tank body (36) communicates with the second plate (36B). The hollows of both intermediate headers (3) and (4) are opened downward by the hole (44) and a part of the refrigerant turn communication part (45) and the opening is closed by the pipe connecting plate (37). Portions (3A) and (4A) are formed. The hollow portions (3A) and (4A) of the two intermediate header portions (3) and (4) are communicated with each other via the refrigerant turn communication portion (45).

  As shown in FIGS. 1 to 4 and 7, the lower header tank (32) has substantially the same configuration as the upper header tank (31), and the same components and the same parts are denoted by the same reference numerals. Both header tanks (31) and (32) are arranged so that the pipe connection plates (37) face each other, and the lower surface covering portion (38) of the upper header tank (31) is the lower header tank (32). It is an upper surface covering part (38). The differences between the lower header tank (32) and the upper header tank (31) are as described below.

Two outward bulging portions (54A) (54B) extending in the left-right direction are formed in the first plate (36A) of the lower header tank (32) at intervals in the front-rear direction. Both the outward bulge portions (54A) and (54B) are respectively the first outward bulge portion (39A) and the third outward bulge portion (39C) of the first plate (36A) of the upper header tank (31). , And the second outer bulging portion (39B) and the fourth outer bulging portion (39D), respectively, are formed from the right end portion to the left end portion of the first plate (36A). The bulge height and width of the front and rear outer bulges (54A) (54B) are the same as the bulges of the outer bulges (39A) to (39D) of the first plate (36A) of the upper header tank (31). It is equal to the height and width. The internal space of the front and rear outward bulging portion (54A) (54B) (54a ) (54b) is adapted to flow the CO ₂ in the lateral direction, respectively, CO ₂ is the front outward bulging portion (54A ) Flows from right to left, and flows from left to right in the inner space (54b) of the rear outward bulge portion (54B). Note that the both outwardly bulged portions (54A) and (54B) are not communicated with each other.

  A plurality of penetrating pipe insertion holes (41) that are long in the front-rear direction are formed in the front and rear side portions of the pipe connection plate (37) at intervals in the left-right direction. 58A) (58B) are provided at intervals in the front-rear direction. The left and right positions of the tube insertion holes (41) of the front and rear tube insertion hole groups (58A) (58B) are the same. All the tube insertion holes (41) of the front tube insertion hole group (58A) are formed within the lateral direction of the front outer bulge portion (54A) of the first plate (36A), and the rear tube insertion hole group The whole tube insertion hole (41) of (58B) is formed within the range in the left-right direction of the rear outer bulge portion (54B).

  Between the pipe insertion holes (41) in the left and right direction of the pipe insertion hole groups (58A) and (B) in the pipe connection plate (37) of the lower header tank (32), that is, heat exchange pipes adjacent in the left and right direction ( 33), a drainage promotion convex portion (59) extending in the front-rear direction and projecting upward is provided. The drainage promotion convex portion (59) is formed by bulging the pipe connection plate (37) upward. Further, the pipe connection plate (37) of the lower header tank (32) at the position corresponding to each pipe insertion hole (41) of both pipe insertion hole groups (58A) (58B), that is, each heat exchange pipe (33). A drainage groove (61) extending in the vertical direction is formed in each side surface covering part (42) of the upper surface covering part (38), and is connected to the drainage groove (61) on both front and rear side edges on the upper surface of the upper surface covering part (38) and is also a heat exchange pipe. A drainage auxiliary groove (62) extending to the (33) side (inward in the front-rear direction) is formed.

  In the second plate (36B) of the tank body (36), the pipe connection plate (37) is formed at a position corresponding to the pipe insertion hole (41), and the pipe insertion hole (41) is connected to each outward bulge ( For all the communication holes (44) communicating with the internal spaces (54a) and (54b) of 54A) and (54B), cut off the portion between the communication holes (44) adjacent in the left-right direction in the second plate (36B). The communication portion (46) formed by And a communicating portion (46) for communicating all the communicating holes (44) leading to the internal spaces (54a) (54b) of the front and rear outwardly bulging portions (54A) (54B) of the first plate (36A), and The central part of the communication hole (44) in the front-rear direction causes the second plate (36B) to move into the inner space (54a) (54b) of the front and rear outer bulges (54A) (54B) of the first plate (36A). Refrigerant circulation portions (55A) and (55B) through which the refrigerant flows in the left-right direction are formed (see FIG. 7).

  Note that the refrigerant inlet (48) and the refrigerant outlet (49) are not formed in the lower header tank (32).

  Corresponding to the two plates (36A) (36B) and the pipe connection plate (37) constituting the tank body (36) of the lower header tank (31), both front and rear outward bulges (54A) (54B) Two intermediate header portions (5) and (6) are formed by the portion to be front and rear. The internal space (54a) (54b) of the front and rear outward bulges (54A) (54B) of the first plate (36A) of the tank body (36) and the refrigerant circulation part (55A) of the second plate (36B) ( 55B), hollow portions (5A) and (6A) of both intermediate header portions (5) and (6) are formed which open upward and are closed by the pipe connecting plate (37).

  The heat exchange pipe (33) is made of a bare metal material, here an aluminum extruded shape, and has a flat shape that is wide in the front-rear direction, and a plurality of refrigerant passages (33a) that extend in the length direction are arranged in parallel in the heat exchange pipe (33). Is formed. Both ends of the heat exchange pipe (33) are inserted into the pipe insertion holes (41) of the header tanks (31) and (32), respectively, and the hollow parts (1A) to (1A) to (6) of the header parts (1) to (6) In a state of protruding into 6A), the pipe connection plate (37) is brazed using the brazing material layer of the pipe connection plate (37). That is, both ends of the heat exchange pipe (33) enter the communication hole (44) to the middle part in the thickness direction of the second plate (36B) (see FIG. 4). The total heat exchange pipe (33) is composed of a plurality of heat exchange pipes (33) arranged in parallel at intervals in the left-right direction, here two heat exchange pipe groups (56A) (56B) ). The upper and lower ends of the plurality of heat exchange tubes (33) located in the right half of the front heat exchange tube group (56A) are inside the hollow portion (1A) of the inlet header portion (1) of the upper header tank (31) and Connected to both header tanks (31) and (32) to communicate with the right side in the hollow portion (5A) of the front intermediate header portion (5) of the lower header tank (32). The upper and lower ends of the heat exchange pipe (33) are inside the hollow part (3A) of the intermediate header part (3) located on the left side of the front side of the upper header tank (31) and the front side intermediate header part of the lower header tank (32). It is connected to both header tanks (31) and (32) so as to communicate with the left part in the hollow part (5A) of (5). The upper and lower ends of the plurality of heat exchange tubes (33) located in the right half of the rear heat exchange tube group (56B) are the hollow portions (2A of the outlet header portion (2) of the upper header tank (31). ) It is connected to both header tanks (31) and (32) so that it leads to the right side in the hollow part (6A) of the rear middle header part (6) in the inner and lower header tanks (32), and also in the left half The upper and lower ends of the plurality of heat exchange pipes (33) positioned in the hollow part (4A) of the intermediate header part (4) located on the left side of the rear side of the upper header tank (31) and the lower header tank (32) It is connected to both header tanks (31) and (32) so as to communicate with the left side portion in the hollow portion (6A) of the rear intermediate header portion (6). A drainage promotion convex portion (59) is provided between the heat exchange tubes (33) adjacent in the left-right direction of the front and rear heat exchange tube groups (56A) (56B).

  The heat exchange pipe (33) was formed by rolling an aluminum brazing sheet having a brazing filler metal layer on both sides, instead of one made of an aluminum extruded profile, and continued through a connecting portion. Two flat wall forming portions, a side wall forming portion integrally formed in a raised shape from the side edge on the opposite side of the connecting portion in each flat wall forming portion, and a predetermined interval in the width direction of the flat wall forming portion. A plate having a plurality of partition wall forming portions integrally formed in a protruding shape from the flat wall forming portion is bent into a hairpin shape at the connecting portion and the side wall forming portions are butted together to form a partition wall. You may use what formed the partition wall by the part.

  The corrugated fin (34) is formed in a wave shape using an aluminum brazing sheet having a brazing filler metal layer on both sides, and a plurality of the corrugated fins (34) are connected in parallel in the front-rear direction to the connecting portion connecting the wave head and the wave bottom. A louver is formed. The corrugated fin (34) is shared by the front and rear heat exchange tube groups (56A) and (56B), and the width in the front and rear direction is the front side of the heat exchange tubes (33) and (33) of the front heat exchange tube group (56A). The distance between the edge and the rear edge of the heat exchange pipes (33), (33) of the rear heat exchange pipe group (56B) is substantially equal. Instead of sharing one corrugated fin (34) between the front and rear heat exchange tube groups (56A) and (56B), the heat exchange tubes (33) adjacent to each other in both heat exchange tube groups (56A) and (56B) Corrugated fins may be arranged between the two.

  Both header tanks (31) and (32) are manufactured as shown in FIGS.

  First, an aluminum brazing sheet having a brazing filler metal layer on both sides is pressed to form a first plate (36A) having outward bulges (39A) (39B) (39C) (39D) (54A) (54B). ). Further, by pressing the aluminum bear material, the second plate (36B) having the communication hole (44), the communication part (45) (46), and the refrigerant circulation part (40A) (40B) (55A) (55B). ). Furthermore, by pressing the aluminum brazing sheet having a brazing filler metal layer on both sides, the lower surface covering part (38), the tube insertion hole (41), the side surface covering part (42) and the side surface covering part (42) are straightened. A pipe connection plate (37) for the upper header tank (31) having the continuous engaging portion forming protrusions (43A) is formed. Further, the upper surface covering portion (38), the tube insertion hole (41), the side surface covering portion (42), the engaging portion forming protrusion (43A) straightly connected to the side surface covering portion (42), the drainage promotion convex portion (59), a pipe connection plate (37) for the lower header tank (32) having a drainage groove (61) and a drainage auxiliary groove (62) is formed. The first header (36A), the second plate (36B) and the pipe connection plate (37) of the upper header tank (31) are formed with right protrusions (36a) (36b) (37a), respectively. Further, a notch (47) is formed in the second plate (36B).

  Next, after the three plates (36A), (36B), and (37) are combined in a laminated form, the protruding piece (43A) is bent to form the engaging portion (43), and the engaging portion (43) is the first plate. Engage with (36A) to make a temporary fix. Then, using the brazing material layer of the first plate (36A) and the brazing material layer of the pipe connecting plate (37), the first plate (36A) and the second plate (36B), the second plate (36B) and the tube The lower surface covering portion (38) or the upper surface covering portion (38) of the connecting plate (37) is brazed to each other, and the side surface covering portion (42) is attached to the second plate (36B) and the first plate (36A). The front and rear side surfaces are brazed, and the engaging portion (43) is brazed to the first plate (36A). Thus, both header tanks (31) and (32) are manufactured.

  The evaporator (30) is prepared by preparing the above-mentioned two temporary fixing bodies when manufacturing the header tanks (31) and (32), a plurality of heat exchange pipes (33) and corrugated fins (34), Temporary fixing bodies are arranged at intervals so that the pipe connection plates (37) face each other, multiple heat exchange pipes (33) and corrugated fins (34) are arranged alternately, heat exchange Insert both ends of the pipe (33) into the pipe insertion holes (41) of the pipe connection plates (37) of both temporary fixing bodies, and attach the side plates (35) to the outside of the corrugated fins (34) at both ends. Arranging the refrigerant inlet / outlet member (51) through the brazing sheet (57) so as to straddle the three plates (36A) (36B) (37), and the three plates (36A ) (36B) (37) are brazed together to form the header tank (31) (32), and at the same time, the heat exchange pipe (33) is attached to the header tank (31) (32). The fins (34) heat exchange tubes (33) and the side plates (35) fin (34), are prepared by respectively brazed to the upper header tank (31) to and out member (51).

  The evaporator (30) constitutes a supercritical refrigeration cycle together with an intermediate heat exchanger for exchanging heat between the refrigerant coming out of the compressor, the gas cooler, the decompressor and the gas cooler and the refrigerant coming out of the evaporator. For example, it is installed in a car.

In the above-described evaporator (30), as shown in FIG. 10, the liquid-phase CO ₂ that has been decompressed through the expansion valve as the decompressor passes through the refrigerant inflow passage (52) of the inlet / outlet member (51). The refrigerant enters the hollow part (1A) of the inlet header part (1) of the upper header tank (31) from the refrigerant inlet (48), and flows into the hollow part (1A) while flowing in the left direction. The refrigerant flows into the refrigerant passages (33a) of all the refrigerant inflow side heat exchange tubes (33) communicating with the inside.

The CO _{2 that} has flowed into the refrigerant passages (33a) of all the refrigerant inflow side heat exchange tubes (33) communicating with the hollow portion (1A) of the inlet header portion (1) moves downward in the refrigerant passage (33a). Flows into the right part of the hollow part (5A) of the front intermediate header part (5) of the lower header tank (32), flows to the left in the hollow part (5A), and flows to the left to divert all the refrigerant. It flows into the refrigerant passage (33a) of the side heat exchange pipe (33).

CO ₂ flowing into the refrigerant passages (33a) of all the refrigerant inflow side heat exchange tubes (33) communicating with the hollow portions (5A) of the front intermediate header portion (5) of the lower header tank (32) Change the flow direction and flow upward in the refrigerant passage (33a) to enter the hollow part (3A) of the front intermediate header part (3) of the upper header tank (31), for the refrigerant turn of the second plate (36B) It passes through the communication part (45) and enters the hollow part (4A) of the rear intermediate header part (4). The CO ₂ flowing into the hollow portion (4A) of the rear intermediate header portion (4) flows into the refrigerant passages (33a) of all the heat exchange tubes (33) communicating with the hollow portion (4A). The flow direction is changed to flow downward in the refrigerant passage (33a) and flow into the left side portion in the hollow portion (6A) of the rear intermediate header portion (6) of the lower header tank (32), and the hollow portion (6A ) Flows in the right direction, divides and flows into the refrigerant passages (33a) of all the refrigerant inflow side heat exchange tubes (33).

The CO ₂ flowing into the refrigerant passages (33a) of all the heat exchange pipes (33) communicating with the hollow portions (6A) of the rear intermediate header portion (6) of the lower header tank (32) flows in the flow direction. To flow upward in the refrigerant passage (33a) and enter the hollow portion (2A) of the outlet header portion (2) of the upper header tank (31) and flow to the right in the hollow portion (2A). It flows out through the refrigerant outlet path (53) of the outlet (49) and the inlet / outlet member (51). While the CO ₂ flows in the refrigerant passage (33a) of the heat exchange pipe (33), heat exchange is performed between the air flowing in the direction indicated by the arrow X in FIGS. 1 and 10 to form a gas phase. Leaked.

  At this time, condensed water is generated on the surface of the corrugated fin (34), and this condensed water flows down to the upper surface of the lower header tank (32) through the corrugated fin (34) and the heat exchange pipe (33). The condensed water that has flowed down to the upper surface of the lower header tank (32) on the rear side (windward side) is the heat of the rear heat exchange tube group (56B) on the upper surface covering portion (38) of the pipe connection plate (37). It flows to the front side through a portion between the exchange pipe (33) and the drainage promotion convex part (59), and further, the heat exchange pipe (33) of the front heat exchange pipe group (56A) and the drainage promotion convex part (59 ) Flows to the front side through the portion between and the lower header tank (32). The condensed water flowing down to the upper surface of the lower header tank (32) on the front side is the heat exchange pipe (33) of the rear heat exchange pipe group (56B) on the upper surface covering part (38) of the pipe connection plate (37). And flows through the portion between the drainage promotion convex portion (59) and the lower header tank (32). The drainage auxiliary groove (62) and the drainage groove (61) smoothly flow downward from the lower header tank (32) of the condensed water. In addition, the condensed water that has flowed down to the upper surface of the lower header tank (32) on the rear side (windward side) is caused by the functions of the auxiliary drainage groove (62) and drainage groove (61) on the lower header tank (32). May flow downward.

  Therefore, an increase in air-side pressure loss due to accumulation of a large amount of condensed water between the upper surface of the lower header tank (32) and the lower end of the corrugated fin (34) is prevented, and as a result, the performance of the evaporator (30) Reduction is prevented. Moreover, before a relatively large amount of condensed water accumulates between the upper surface of the lower header tank (32) and the end of the corrugated fin (34), the heat exchange pipe (33) and the drainage promotion convex portion (59) When a small amount of condensed water accumulates, the condensed water is pushed forward by the wind and flows down the lower header tank (32), so that the condensate is effectively scattered from the lower header tank (32). Is prevented.

  In the above embodiment, the number of the second plates (36B) of the tank body (36) is 1, but the number of the second plates (36B) is not limited to this, and the first plate (36A) and the pipe connection plate (37) A plurality of second plates (36B) may be interposed between them in the middle. In this case, a communication hole (44), a communication part (45) (46), etc. are formed in each 2nd plate (36B).

  Moreover, in the said embodiment, although the heat exchanger by this invention is applied to the evaporator of a supercritical refrigeration cycle, it is not restricted to this, The heat exchanger by this invention is provided for another use. Sometimes.

Furthermore, in the above embodiment, CO ₂ is used as the supercritical refrigerant in the supercritical refrigeration cycle, but is not limited to this, and ethylene, ethane, nitric oxide, or the like is used.

1 is a partially cutaway perspective view showing an overall configuration of an evaporator to which a heat exchanger according to the present invention is applied. FIG. 2 is a partially omitted vertical sectional view of the gas cooler of FIG. It is an AA line expanded sectional view of FIG. FIG. 3 is an enlarged sectional view taken along line B-B in FIG. 2. It is CC sectional view taken on the line of FIG. It is a disassembled perspective view which shows the right end part of the upper header tank in the evaporator of FIG. It is the DD sectional view taken on the line of FIG. It is a disassembled perspective view which shows the part of the upper header tank of the evaporator of FIG. It is a disassembled perspective view which shows the part of the lower header tank of the evaporator of FIG. It is a figure which shows the flow of the refrigerant | coolant in the evaporator of FIG.

Explanation of symbols

(30): Evaporator
(31): Upper header tank
(32): Lower header tank
(33): Heat exchange pipe
(34): Corrugated fin
(36): Tank body
(36A): 1st plate
(36B): Second plate
(37): Pipe connection plate
(38): Top cover
(39A) (39B) (39C) (39D): Outward bulge
(41): Tube insertion hole
(42): Side cover
(44): Communication hole
(59): Convex part for drainage promotion
(56A) (56B): Heat exchange tube group
(61): Drainage channel
(62): Drainage auxiliary groove

Claims (8)

A pair of header tanks arranged in the left-right direction spaced apart in the vertical direction, a plurality of heat exchange tubes arranged in the left-right direction between the two header tanks, and heat exchange adjacent in the left-right direction An evaporator comprising a tank main body and a pipe connecting plate having an upper surface covering portion that covers the upper surface of the tank main body.
An evaporator in which a drainage promotion convex portion extending in the front-rear direction and projecting upward is provided between the heat exchange tubes adjacent in the left-right direction on the outer surface of the upper surface covering portion of the pipe connection plate. A plurality of heat exchange tube groups composed of a plurality of heat exchange tubes arranged at intervals in the left-right direction are provided at intervals in the front-rear direction, and heat adjacent to the left-right direction of the heat exchange tube group at the front end portion. The evaporator according to claim 1, wherein a drainage promotion convex portion is provided between the exchange pipes. A plurality of heat exchange tube groups composed of a plurality of heat exchange tubes arranged at intervals in the left-right direction are provided at intervals in the front-rear direction, and the heat exchange tubes adjacent to each other in the left-right direction of each heat exchange tube group The evaporator according to claim 1, wherein a drainage promoting convex portion is provided therebetween. The evaporator according to any one of claims 1 to 3, wherein the drainage promotion convex portion is formed by causing the pipe connection plate to bulge upward. The evaporator according to any one of claims 1 to 4, wherein a drainage groove extending in the vertical direction is formed in a portion corresponding to each heat exchange pipe on the front side surface of the lower header tank. The evaporator according to claim 5, wherein a drainage auxiliary groove is formed on the upper surface of the lower header tank so as to continue to the upper end of the drainage groove and extend toward the heat exchange pipe. The pipe connection plate of the lower header tank is connected to the front and rear side edges of the upper surface covering portion and has a side surface covering portion that covers both the front and rear side surfaces of the tank body, and a drainage groove is formed in the side surface covering portion. The evaporator according to claim 6, wherein a drainage auxiliary groove is formed in the upper surface covering portion. The tank body of the lower header tank has a first plate having at least one outward bulging portion extending in the left-right direction, and the outer bulging portion of the first plate between the pipe connecting plate and the first plate. A plurality of tube insertion holes are formed in the portion corresponding to the outward bulge portion of the pipe connection plate, and are provided with a second plate that is interposed so as to close the opening and joined to both plates. A through hole is formed in the second plate of the tank main body so as to penetrate each tube insertion hole of the pipe connection plate into the outward bulging portion of the first plate. The evaporator according to any one of claims 1 to 7, wherein both ends of the heat exchange pipe are inserted into the pipe insertion holes of the pipe connection plates of both header tanks and brazed to the pipe connection plate.

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