JP2005241168A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger with a structure capable of discharging condensate remaining at a downstream side end part of an air flowing direction of a fold-back part of a corrugated fin, and preventing a brazing material of a tank from flowing into a groove of a tube when brazing the tube to the tank. <P>SOLUTION: In the heat exchanger, an end 12b of downstream side of the air flowing direction of an outer fin (corrugated fin) 12 of a groove 20 of downstream side end part in the air flow direction of the tube 11 is brought into a same position of an end 20a of upstream side of the air flowing direction, one or both ends of the downstream side in the air flowing direction of the outer fin are provided with protruding parts. The width of the outer fin in the air flowing direction including the width of the protruding parts in the air flowing direction is made equal to the width of the tube in the air flowing direction and the protruding parts are only provided at flat surface parts of the corrugated fin. At a brazing and mating part of the tube and the tank, an end of the groove is provided off a tip end position of a brazing fillet and a forming range of the groove is matched with a range of mating length of the corrugated fin. <P>COPYRIGHT: (C)2005,JPO&amp;NCIPI

Description

  The present invention relates to a heat exchanger, and specifically, is configured to reliably drain condensed water generated during operation (during cooling of air by a refrigerant) in a heat exchanger that functions as an evaporator.

  A heat exchanger used as an evaporator of a vehicle air conditioner (so-called car air conditioner) has a flat tube in which a refrigerant flow path along the vertical direction is formed, and a tube joined to the surface of the tube together with the tube It is a laminated type in which a large number of corrugated fins forming an air flow path along the horizontal direction are alternately stacked, and performs heat exchange between the refrigerant flowing through the refrigerant flow path and the air flowing through the air flow path. .

  When such a heat exchanger functions as an evaporator, when the air is cooled by heat exchange between the refrigerant and the air, moisture contained in the air is condensed to produce condensed water, and this condensed water is It may adhere and stay on the surface of the tube or corrugated fin. In some cases, the accumulated condensed water may increase the ventilation resistance of the air flow path, or may be blown into the room by the ventilation. For example, in a vehicle air conditioner, condensed water blown off by ventilation is blown into the vehicle compartment from a blow-out port of the front grille. In particular, at present, heat exchangers tend to be miniaturized, and the proportion of condensed water is larger than the total volume of the heat exchanger, so it is important to improve the drainage of condensed water.

  For this reason, it is important to improve the drainage of condensed water in a heat exchanger that functions as an evaporator. On the other hand, conventional heat exchangers (evaporators) that improve the drainage of condensed water include those shown in FIGS. 9 and 10, for example (see Patent Document 1 below). 9 and 10 are a perspective view and a plan view showing an end of the conventional evaporator on the downstream side in the air flow direction.

  As shown in FIGS. 9 and 10, the conventional evaporator is a laminated type obtained by alternately laminating flat tubes 1 and outer fins 4 that are corrugated fins (wave-shaped fins). . Each tube 1 is formed by joining two plates 2 formed by pressing an aluminum material so as to face each other with an inner fin 8 being an aluminum corrugated fin interposed therebetween. . At this time, inside the tube 1, a refrigerant flow path 3 is formed along the vertical direction with the concave portions 6 on the inner surface side (opposing surface side) of the two plates 2 formed by the press working facing each other. Yes. Moreover, the groove | channel which is a recessed part of the outer surface side (anti-opposing surface side) of the plate 2 formed by the said press work in the downstream edge part of the air flow direction (horizontal direction: arrow A direction) in the surface of the tube 1 7 is provided along the up-down direction (arrow B direction).

  On the other hand, on the outside of the tube 1, an air flow path 5 is formed along the horizontal direction by the tube 1 and the corrugated fins 4. Further, a louver 4c is formed on the flat portion 4a of the corrugated fin 4 by cutting and raising a part of the flat portion 4a. These louvers 4 c mean that the air flowing through the air flow path 5 meanders on both the upper and lower sides of the flat portion 4 a, thereby further improving the heat exchange efficiency between the air and the refrigerant flowing through the refrigerant flow path 3 of the tube 1. Is provided.

  In this evaporator, the depth H of the groove 7 is set to 0.9 ± 0.2 mm, and the louver cutting position L is set to 0 to 0.6 mm, whereby the condensed water is directed to the groove 7 by the louver 5. Thus, the condensed water can be drained by the groove 7 while ensuring a sufficient suction force to be turned, and the drainage of the condensed water is improved.

JP-A-11-83371

  However, even if the above-described conventional configuration is adopted, for example, if the proportion of condensed water increases due to downsizing of the heat exchanger or improvement of cooling performance, the air flow direction in the folded portion of the corrugated fin 4 as shown in FIG. Condensed water 9 may accumulate at the downstream end 4b. However, as shown in FIGS. 9 and 10, since the end 4b of the corrugated fin 4 completely crosses the groove 7, when the condensed water 9 is accumulated in the end 4b, the accumulated condensation The water 9 cannot be drained by the groove 7, and there is a possibility that the condensed water 9 having no place to go is blown into the room by ventilation. When the tube 1 and the corrugated fin 4 are laminated, generally, the corrugated fin 4 is positioned with respect to the tube 1 by applying the end of the tube 1 and the end of the corrugated fin 4 to the abutting plate 10 as shown in FIG. For this reason, the end 4 b of the corrugated fin 4 straddles the groove 7 of the tube 1.

  In addition, there is no particular problem when the tube and the tank provided at the upper end and the lower end of the tube are integrally formed. However, for example, when the tube is extruded, the tube and the tank are separated. In this case, it is necessary to braze the tube to the tank. At this time, if the groove provided at the downstream end of the tube in the air flow direction is too long (for example, if the groove is provided over the entire length of the tube), the tube is When the brazing material of the tank that has reached a high temperature flows into the tube groove when it is brazed to the tube, erosion may occur in the groove portion, which may cause problems such as thinning or perforation. .

  Therefore, in view of the above circumstances, the present invention can drain the condensed water staying at the downstream end of the corrugated fin folded portion in the air flow direction, and when brazing the tube to the tank, the brazing material of the tank It is an object of the present invention to provide a heat exchanger having a structure capable of preventing the air from flowing into the groove of the tube.

  A heat exchanger according to a first aspect of the present invention that solves the above problems includes a flat tube in which a refrigerant flow path along the vertical direction is formed, and an air flow along the horizontal direction together with the tube that is joined to the surface of the tube. Corrugated fins that form channels are alternately stacked, and in a heat exchanger that exchanges heat between the refrigerant flowing through the refrigerant flow path and the air flowing through the air flow path, the air flow direction on the surface of the tube A groove along the vertical direction is formed at the downstream end, and the downstream end of the corrugated fin in the air flow direction is positioned upstream of the downstream end of the groove in the air flow direction. As a result, the condensed water accumulated at the downstream end of the corrugated fin folded-back portion is drawn by the condensed water flowing downward in the groove and enters the groove downward together with the condensed water. It is characterized by being configured to be drained.

  The heat exchanger according to a second aspect of the present invention is the heat exchanger according to the first aspect of the present invention, wherein the corrugated fin has a plurality of convex portions at the downstream end in the air flow direction, and the air flow direction of these convex portions is The width of the corrugated fin including the width in the air flow direction is made to coincide with the width of the tube in the air flow direction.

  Further, the heat exchanger of the third invention is the heat exchanger of the first invention, wherein the corrugated fin has a plurality of convex portions at an end on the downstream side in the air flow direction and an end on the upstream side in the air flow direction, The width in the air circulation direction of the corrugated fin including the width in the air circulation direction of the convex portions on both sides is made to coincide with the width in the air circulation direction of the tube.

  Moreover, the heat exchanger of 4th invention is a heat exchanger of 2nd or 3rd invention, The said convex part was provided only in the plane part of the said corrugated fin, It is characterized by the above-mentioned.

  The heat exchanger according to the fifth aspect of the invention is a flat tube in which a refrigerant flow path along the vertical direction is formed inside, and an air flow path along the horizontal direction together with the tube that is joined to the surface of the tube. And a corrugated fin that is alternately stacked, and in a heat exchanger that performs heat exchange between the refrigerant flowing through the refrigerant flow path and the air flowing through the air flow path, on the downstream side of the air flow direction on the surface of the tube A groove along the vertical direction is formed at the end, and the upper end or lower end of the tube or the upper end and the lower end are joined to the tank by brazing, and the tube and the tank are brazed. The portion is characterized in that the upper end position or the lower end position or the upper end position and the lower end position of the groove are separated from the front end position of the brazing fillet.

  The heat exchanger of the sixth invention is the heat exchanger of the first, second, third or fourth invention, wherein the upper end or lower end of the tube or the upper and lower ends are joined to the tank by brazing. The upper end position or the lower end position or the upper end position and the lower end position of the groove are separated from the front end position of the brazing fillet at the brazed joint portion between the tube and the tank.

  The heat exchanger of the seventh invention is characterized in that, in the heat exchanger of the fifth or sixth invention, the formation range of the groove is made to coincide with the range of the junction length of the corrugated fins.

  According to the heat exchanger of the first invention, a groove along the vertical direction is formed at the end of the tube surface on the downstream side in the air flow direction, and the end of the corrugated fin on the downstream side in the air flow direction is By positioning the corrugated fins at the downstream end of the air flow direction, the condensed water collected at the downstream end of the corrugated fin is drawn to the condensed water flowing down the groove. Since it is configured so as to enter the groove and flow downward along with the condensed water to be drained, the drainage of the condensed water is improved. That is, when this heat exchanger functions as an evaporator, when the air is cooled by heat exchange between the refrigerant flowing through the refrigerant flow path in the tube and the air flowing through the air flow path of the corrugated fin portion, Even if the condensed water generated by the condensation of the contained water accumulates at the downstream end of the corrugated fin in the air flow direction, the accumulated condensed water is condensed water (tube or The condensed water adhering to the surface of the corrugated fins is pushed by the air and is drawn by the condensed water accumulated in the groove), enters the groove, flows downward together with the condensed water, and is efficiently drained. For this reason, generation | occurrence | production of malfunctions, such as the condensed water collected at the edge part of the corrugated fin being blown away indoors by ventilation, can be prevented.

  According to the heat exchanger of the second aspect of the present invention, the corrugated fin has an air flow direction in the air flow direction of the corrugated fin, including a plurality of convex portions at the downstream end in the air flow direction, Therefore, the corrugated fin can be easily positioned with respect to the tube by, for example, placing the end of the tube and the end (convex part) of the corrugated fin against the backing plate. This can improve the positioning accuracy of the corrugated fin.

  According to the heat exchanger of the third aspect of the invention, the corrugated fin has a plurality of convex portions at the downstream end in the air flow direction and the upstream end in the air flow direction, and the convex portions on both sides of the air flow direction. Since the width of the corrugated fin including the width in the air flow direction is matched with the width of the tube in the air flow direction, the tube can be easily placed by applying the end of the tube and the end of the corrugated fin (projection) to the backing plate. The corrugated fins can be positioned with respect to the positioning accuracy of the corrugated fins, and the corrugated fins have the same structure on both sides. Since it can be set in any direction, there is a degree of freedom of applicable models.

  According to the heat exchanger of the fourth invention, since the convex portion is provided only on the flat portion of the corrugated fin, the convex portion does not straddle the groove at all, so that the corrugated fin has an air flow direction downstream end. The drainage of the accumulated condensed water is further improved.

  According to the heat exchanger of the fifth invention or the sixth invention, the upper end position or the lower end position or the upper end position and the lower end position of the groove are separated from the front end position of the brazing fillet at the brazed joint between the tube and the tank. It is possible to prevent erosion from occurring due to the brazing material of the tank flowing into the grooves during brazing.

  According to the heat exchanger of the seventh aspect of the invention, since the groove formation range is matched with the range of the corrugated fin joining length, the length of the groove required for draining condensed water is ensured.

  Embodiments of the present invention will be described below in detail with reference to the drawings. The heat exchanger described below is used as a heat exchanger of an air conditioner, and may be a heat exchanger used only as an evaporator of a vehicle air conditioner or the like, and the flow of refrigerant It may be a heat exchanger that may function as an evaporator or function as a condenser by switching directions.

<Embodiment 1>
FIG. 1 is a perspective view showing a part of a heat exchanger according to Embodiment 1 of the present invention, and FIGS. 2 and 3 are a perspective view and a plan view showing an enlarged part of the heat exchanger. .

  As shown in FIGS. 1 and 2, the heat exchanger according to the first embodiment has a flat tube 11 and a plurality of outer fins 12 that are corrugated fins (wave-shaped fins) alternately stacked. It is a laminated type. The outer fin 12 is made of aluminum, and the folded portion is joined to the surface of the tube 11 by brazing.

  Each tube 11 is formed by brazing and joining two plates 14 formed by pressing an aluminum material so as to face each other with an inner fin 13 that is an aluminum corrugated fin sandwiched therebetween. It is. At this time, inside the tube 11, the recess 15 on the inner surface side (opposite surface side) of the two plates 14 formed by the pressing process is opposed to each other, and a coolant channel 16 is formed along the vertical direction. Yes. In the illustrated example, the recess 15 has a trapezoidal cross-sectional shape, and the refrigerant channel 16 has a hexagonal cross-sectional shape.

  Moreover, the groove | channel which is a recessed part of the outer surface side (anti-opposing surface side) of the plate 14 formed by the said press work in the downstream edge part of the air flow direction (horizontal direction: arrow C direction) in the surface of the tube 11 20 is provided along the up-down direction (arrow D direction). The width W of the cross section (air flow direction) of the groove 20 is, for example, about 1 to 2 mm. The cross-sectional shape of the groove 20 is a trapezoidal shape in the illustrated example, but is not necessarily limited thereto, and may be an arc shape or a rectangular shape. In the illustrated example, the groove 20 is provided not only at the downstream end portion in the air circulation direction on the surface of the tube 11 but also at the central portion in the air circulation direction and the upstream end portion in the air circulation direction.

  In addition, a tank 18 is provided at the upper end of the tube 11. The tank 18 is integral with the tube 11, and is integrally formed by laminating a large number of tank portions 14a formed at the upper end portion of the plate 14 by the press working. In the illustrated example, the tank is provided only at the upper end of the tube. However, the present invention is not necessarily limited to this, and a heat exchanger in which the tank is provided at the lower end of the tube or both upper and lower ends of the tube are provided. The present invention can also be applied to a heat exchanger provided in the section.

  On the other hand, an air flow path 17 along the horizontal direction is formed by the tube 11 and the outer fin 12 outside the tube 11. In the air flow path 17, air blown by a fan (not shown) flows in the air circulation direction (arrow C direction). As a result, this air and the refrigerant flowing in the vertical direction (arrow D direction) through the refrigerant flow path 16 of the tube 11 exchange heat through the tube 11 and the outer fin 12. Further, a louver 12f is formed on the flat surface portion 12a of the outer fin 12 by cutting and raising a part of the flat surface portion 4a. These louvers 12f meander the air flowing through the air flow path 17 to both the upper and lower sides of the flat portion 12a, thereby further improving the heat exchange efficiency between the air and the refrigerant flowing through the refrigerant flow path 16 of the tube 11. In addition, this invention is not necessarily limited to this, It can apply also to the heat exchanger with which the louver is not provided in the outer fin (corrugated fin).

  As shown in FIGS. 1 to 3, in this heat exchanger, the downstream end 12 b of the outer fin 12 in the air circulation direction is connected to the upstream side in the air circulation direction of the groove 20 at the downstream end of the tube 11 in the air circulation direction. It is made to correspond to the edge 20a. That is, the end 12 b of the outer fin 12 faces the groove 20 at the downstream end of the tube 11 in the air flow direction. As shown in FIG. 2, the end 12 c on the upstream side in the air flow direction of the outer fin 12 is made to coincide with the end 20 b on the upstream side in the air flow direction in the groove 20 at the upstream end of the tube 11 in the air flow direction.

  As described above, according to the heat exchanger of the first embodiment, the end 12b on the downstream side in the air flow direction of the outer fin 12 is connected to the air flow direction in the groove 20 at the downstream end of the tube 11 in the air flow direction. Since it was made to correspond to the upstream end 20a, the drainage of condensed water improves. That is, when this heat exchanger functions as an evaporator, when the air is cooled by heat exchange between the refrigerant flowing through the refrigerant flow path 16 in the tube 11 and the air flowing through the air flow path 17 of the outer fin 12 portion. The condensed water produced by the condensation of the water contained in the air is swept away by the air and the downstream end of the folded portion of the outer fin 12 in the air flow direction as shown by the one-dot chain line in FIGS. Even if accumulated in the portion 12d, the accumulated condensed water 21 flows downward in the groove 20 as indicated by an arrow E (condensed water adhering to the surface of the tube 11 and the outer fin 12 is pushed away by the air and grooved). (Condensed water collected at 20) is drawn into the groove 20 as indicated by the arrow F, flows downward together with the condensed water 22 and is efficiently drained, and enters a drain receiver (not shown). For this reason, generation | occurrence | production of malfunctions, such as the condensed water 21 collected at the edge part 12d of the outer fin 12, being blown away indoors by ventilation, can be prevented.

  Note that the position of the end 12b of the outer fin 12 on the downstream side in the air flow direction is not necessarily the same as the end 20a on the upstream side in the air flow direction of the groove 20 at the downstream end of the tube 11 in the air flow direction. It is not limited, and it is only necessary that the end 12d of the outer fin 12 does not completely straddle the groove 20. For example, as shown by a two-dot chain line in FIG. The position may be on the upstream side, and conversely the position on the downstream side in the air flow direction from the end 20a of the groove 20 may be used. That is, the end 12b of the outer fin 12 on the downstream side in the air flow direction is positioned on the upstream side of the groove 20 in the air flow direction with respect to the end 20c on the downstream side in the air flow direction. Condensed water 21 collected at the end 12 d on the downstream side in the direction is drawn by the condensed water 22 flowing downward in the groove 20, enters the groove 20, flows downward together with the condensed water 22, and is drained. That's fine.

<Embodiment 2>
FIG. 4A is a configuration diagram of an aluminum material for forming an outer fin of a heat exchanger according to Embodiment 2 of the present invention, and FIG. 4B is a perspective view showing the configuration of the outer fin. 4 (c) is a perspective view showing another configuration of the outer fin.

  As shown in FIG. 4A, the band-plate-like aluminum material 31 for forming the outer fin has convex portions 31a formed at appropriate intervals at one end in the width direction. Therefore, as shown in FIG. 4 (b), the outer fin (corrugated fin) 12 of the present embodiment 2 formed by forming this aluminum material 31 into a waveform with a molding machine such as a gear-shaped roll (not shown) A plurality of convex portions 12e (the convex portions 31a of the aluminum material 31) are provided at the downstream end 12b in the air circulation direction (arrow C direction). And the width WF of the air circulation direction of the outer fin 12 including the width of the air flow direction of these convex portions 12e is made to coincide with the width WT (for example, about 40 to 60 mm) of the tube 11 in the air circulation direction.

  In addition, in FIG.4 (b), since the convex part 12e may be provided also in the folding | returning part of the outer fin 12, and the convex part 12e will straddle the groove | channel 20 of the tube 11 in this part, other Compared to the portion, the condensed water collected at the end 12d on the downstream side in the air flow direction of the folded portion of the outer fin 12 may be difficult to drain. Therefore, more desirably, as shown in FIG. 4C, the convex portion 12 e is provided only on the flat surface portion 12 a of the outer fin 12.

  Since the configuration of the heat exchanger of the second embodiment other than the outer fin 12 is the same as that of the heat exchanger of the first embodiment, illustration and description thereof are omitted here (FIGS. 1 to 1). 3).

  As described above, according to the heat exchanger of the second embodiment, the end 12b of the outer fin 12 on the downstream side in the air flow direction has the plurality of convex portions 12e, and the air flow of these convex portions 12e. Since the width WF in the air circulation direction of the outer fin 12 including the width in the direction is made to coincide with the width WT in the air circulation direction of the tube 11, the end of the tube 11 and the end of the outer fin 12 (projection 12 e) are applied. The outer fin 12 can be easily positioned with respect to the tube 11 by applying it to the plate, and the positioning accuracy of the outer fin 12 is improved.

  Moreover, since the convex part 12e does not straddle the groove | channel 20 at all when the convex part 12e is provided only in the plane part 12a of the outer fin 12, the folding | returning part of the outer fin 12 is the downstream of the air circulation direction. The drainage of the condensed water collected at the end 12d is further improved.

<Embodiment 3>
FIG. 5A is a configuration diagram of an aluminum material for forming an outer fin of a heat exchanger according to Embodiment 3 of the present invention, and FIG. 5B is a perspective view showing the configuration of the outer fin. FIG. 5C is a perspective view showing another configuration of the outer fin.

  As shown in FIG. 5A, in the third embodiment, convex portions 31a are formed at appropriate intervals on both ends of the aluminum material 31 in the width direction. Therefore, as shown in FIG. 5 (b), the outer fin (corrugated fin) 12 of the third embodiment formed by forming this aluminum material 31 into a corrugated shape with a molding machine such as a gear-shaped roll (not shown) The air flow direction (arrow C direction) downstream end 12b and the air flow direction upstream end 12c each have a plurality of convex portions 12e (the convex portions 41a of the aluminum material 41). The width WF in the air circulation direction of the outer fin 12 including the width in the air circulation direction of the convex portions 12e on both sides is made to coincide with the width WT of the tube 11 in the air circulation direction.

  In addition, in FIG.5 (b), since the convex part 12e may be provided also in the folding | turning part of the outer fin 12, and the convex part 12e will straddle the groove | channel 20 of the tube 11 in this part, other Compared to the portion, the condensed water collected at the end 12d on the downstream side in the air flow direction of the folded portion of the outer fin 12 may be difficult to drain. Therefore, more desirably, the convex portion 12e is provided only on the flat surface portion 12a of the outer fin 12, as shown in FIG.

  Since the configuration other than the outer fin 12 in the heat exchanger of the third embodiment is the same as that of the heat exchanger of the first embodiment, illustration and description thereof are omitted (FIGS. 1 to 1). 3).

  As described above, according to the heat exchanger of the third embodiment, the outer fin 12 has the plurality of convex portions 12e at the downstream end 12b in the air circulation direction and the upstream end 12b in the air circulation direction. Since the width WF in the air flow direction of the outer fin 12 including the width in the air flow direction of the convex portions 12e on both sides is made to coincide with the width WT in the air flow direction of the tube 11, the end of the tube 11 and the outer fin The outer fin 12 can be easily positioned with respect to the tube 11 by, for example, applying the end of 12 (the convex portion 12e) to the contact plate, and the positioning accuracy of the outer fin 12 is improved. In addition, since both sides of the outer fin 12 have the same structure, the direction of air flow is not limited to one direction (arrow C direction), and the direction can be reversed. .

  Moreover, since the convex part 12e does not straddle the groove | channel 20 at all when the convex part 12e is provided only in the plane part 12a of the outer fin 12, the folding | returning part of the outer fin 12 is the downstream of the air circulation direction. The drainage of the condensed water accumulated at the end 12b is further improved.

<Embodiment 4>
6 is a front view showing a part of a heat exchanger according to Embodiment 4 of the present invention, FIG. 7 is an enlarged perspective view of a part of the heat exchanger, and FIG. 8 is the heat exchanger. It is an expanded sectional view which shows the brazing part of the upper end part of a tube, and a lower end part.

  As shown in FIGS. 6 and 7, the heat exchanger according to the fourth embodiment has a flat tube 51 and a plurality of outer fins 52 that are corrugated fins (wave-shaped fins) alternately stacked. It is a laminated type. The outer fin 52 is made of aluminum, and the folded portion is joined to the surface of the tube 51 by brazing. Each tube 1 is made of extruded aluminum. At this time, a refrigerant flow path 53 is formed in the tube 51 along the vertical direction by the extrusion molding. In the illustrated example, the cross-sectional shape of the refrigerant channel 53 is rectangular.

  Further, a groove 54 formed later by pressing or the like is formed along the vertical direction (arrow H direction) at the downstream end of the air flow direction (horizontal direction: arrow G direction) on the surface of the tube 51. Is provided. The width W of the cross section (air flow direction) of the groove 54 is, for example, about 1 to 2 mm. The cross-sectional shape of the groove 54 is a trapezoidal shape in the illustrated example, but is not necessarily limited to this, and may be an arc shape or a rectangular shape. In the illustrated example, the groove 54 is provided not only at the downstream end portion in the air circulation direction on the surface of the tube 51 but also at the central portion in the air circulation direction and the upstream end portion in the air circulation direction.

  As shown in FIG. 7, in the present heat exchanger, an end 52 b on the downstream side in the air flow direction of the outer fin 52 is connected to an end 54 a on the upstream side in the air flow direction in the groove 54 at the downstream end portion in the air flow direction of the tube 51. To match. That is, the end 52 b of the outer fin 52 faces the groove 54 at the downstream end of the tube 51 in the air flow direction. The upstream end 52c of the outer fin 52 in the air flow direction is made to coincide with the upstream end 54b of the groove 54 at the upstream end of the tube 51 in the air flow direction.

  On the other hand, an air flow path 60 extending in the horizontal direction is formed on the outside of the tube 51 by the tube 51 and the outer fin 52. In the air flow path 60, air blown by a fan (not shown) flows in the air circulation direction (arrow G direction). As a result, the air and the refrigerant flowing in the vertical direction (in the direction of arrow H) through the refrigerant flow path 53 of the tube 51 exchange heat through the tube 51 and the outer fin 52. Further, a louver 52e is formed on the flat surface portion 52a of the outer fin 52 by cutting and raising a part of the flat surface portion 52a. These louvers 52e meander the air flowing through the air flow path 60 to the upper and lower sides of the flat portion 52a, thereby further improving the heat exchange efficiency between the air and the refrigerant flowing through the refrigerant flow path 53 of the tube 51. In addition, this invention is not necessarily limited to this, It can apply also to the heat exchanger with which the louver is not provided in the outer fin (corrugated fin).

  Further, an upper tank 55 and a lower tank 56 are respectively provided at the upper end portion and the lower end portion of the tube 51. The upper end portion and the lower end portion of the tube 51 are joined to the upper tank 55 and the lower tank 56 by brazing, respectively. That is, as shown in FIG. 8, the joint between the upper end of the tube 51 and the upper tank 55 has a fillet 57 formed at the time of brazing, and the lower end of the tube 51 and the lower tank 56 are formed. The joint portion has a fillet 58 formed at the time of brazing. The height from the base end to the tip end of the fillets 57, 58 is, for example, about 2 mm.

  As shown in FIGS. 6 and 8, in the present heat exchanger, the formation range of the groove 54 of the tube 51 is matched not with the entire length of the tube but with the range of the joining length L with the outer fin 52. That is, by this, the position of the upper end 54d of the groove 54 is separated from the position of the tip (lower end) 57a of the brazing fillet 57, and the position of the lower end 54e of the groove 54 is set to the position of the tip (upper end) 58a of the brazing fillet 58. Away from That is, a clearance CL is provided between the brazing fillets 57 and 58 and the groove 54.

  As described above, according to the heat exchanger of the fourth embodiment, the end 52b of the outer fin 52 on the downstream side in the air flow direction is connected to the air flow direction in the groove 54 at the downstream end of the tube 51 in the air flow direction. Since it was made to correspond to the upstream end 54a, the drainage of condensed water improves. That is, when this heat exchanger functions as an evaporator, when the air is cooled by heat exchange between the refrigerant flowing through the refrigerant flow path 53 in the tube 51 and the air flowing through the air flow path 60 of the outer fin 52 portion. The condensed water generated by the condensation of the water contained in the air is pushed into the air and flows to the end 52d on the downstream side in the air flow direction in the folded portion of the outer fin 52 as shown by a one-dot chain line in FIG. Even if it accumulates, the accumulated condensed water 61 flows downward in the groove 54 as indicated by an arrow I (condensed water adhering to the surfaces of the tube 51 and the corrugated fin 52 is pushed away by the air and accumulated in the groove 54. The condensed water) is drawn as shown by an arrow J, enters the groove 54, flows downward together with the condensed water 62, and is efficiently drained, and enters a drain receiver (not shown). For this reason, the generation | occurrence | production of malfunctions, such as the condensed water 61 collected in the edge part 52d of the outer fin 52 being blown away indoors by ventilation, can be prevented.

  The position of the end 52b of the outer fin 52 on the downstream side in the air flow direction is not necessarily equal to the end 54a on the upstream side in the air flow direction of the groove 54 at the downstream end of the tube 51 in the air flow direction. It is not limited, and it is only necessary that the end 52d of the outer fin 52 does not completely cross the groove 54 (see FIG. 3). That is, the air flow in the folded portion of the outer fin 52 is determined by positioning the downstream end 52b of the outer fin 52 in the air flow direction upstream of the end 54c of the groove 54 in the air flow direction. Condensed water 61 accumulated at the end 52 d on the downstream side in the direction is drawn by the condensed water 62 flowing downward in the groove 54, enters the groove 54, flows downward together with the condensed water 62, and is drained. That's fine. Also in the fourth embodiment, a convex portion is formed at one or both ends of the outer fin 52 in the air flow direction as in the second or third embodiment, and the width of the convex portion in the air flow direction is increased. You may make it make the width | variety of the air distribution direction of the included outer fin 52 correspond with the width | variety of the air distribution direction of the tube 51. FIG.

  According to the heat exchanger of the fourth embodiment, since the upper end position 54d and the lower end position 54e of the groove 54 are separated from the front end positions 57a and 58a of the braze fillets 57 and 58, the upper tank 55 and the lower tank It can be prevented that 56 brazing materials flow into the grooves 54 during brazing and cause erosion. In addition, since the formation range of the groove 54 is matched with the range of the joining length L of the outer fin 52, the length of the groove 54 required for draining condensed water can be ensured.

  In the illustrated example, the tanks are provided at the upper and lower ends of the tube, but the present invention is not necessarily limited to this, and the heat exchanger is provided with the tank only at either the upper end or the lower end of the tube. It can also be applied to.

  The present invention relates to a heat exchanger. In an air conditioner, the present invention is applied to a heat exchanger used only as an evaporator, and functions as an evaporator by switching the flow direction of refrigerant and as a condenser. It can also be applied to heat exchangers that may function.

It is a perspective view which shows a part of heat exchanger which concerns on Example 1 of Embodiment of this invention. It is a perspective view which expands and shows further a part of the said heat exchanger. It is a top view which expands and shows further a part of the said heat exchanger. (A) is a block diagram of the aluminum material for shape | molding the outer fin of the heat exchanger which concerns on Embodiment 2 of this invention, (b) is a perspective view which shows the structure of the said outer fin, (c) is the said It is a perspective view which shows the other structure of an outer fin. (A) is a block diagram of the aluminum material for shape | molding the outer fin of the heat exchanger which concerns on Embodiment 3 of this invention, (b) is a perspective view which shows the structure of the said outer fin, (c) is the said It is a perspective view which shows the other structure of an outer fin. It is a front view which shows a part of heat exchanger which concerns on Example 4 of Embodiment of this invention. It is a perspective view which expands and shows further a part of the said heat exchanger. It is an expanded sectional view which shows the brazing part of the upper end part and lower end part of the tube in the said heat exchanger. It is a perspective view which shows the edge part of the air flow direction downstream side of the conventional evaporator. It is a top view which shows the edge part of the air distribution direction downstream of the conventional evaporator.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Tube 12 Outer fin 12a Plane part 12b, 12c End 12d End part 12e Convex part 12f Louver 13 Inner fin 14 Plate 14a Tank part 15 Recessed part 16 Refrigerant flow path 17 Air flow path 18 Tank 20 Groove 20a, 20b, 20c End 21, 22 Condensed water 31 Aluminum material 31a Convex part 51 Tube 52 Outer fin 52a Plane part 52b, 52c End 52d End part 52e Louver 53 Refrigerant flow path 54 Groove 54a, 54b, 54c End 54d Upper end 54e Lower end 55 Upper tank 57 Lower tank 57 Attached fillet 57a Tip 58 Brazed fillet 58a Tip 60 Air flow path 61, 62 Condensed water

Claims (7)

A flat tube in which a refrigerant flow path along the vertical direction is formed inside and corrugated fins that are joined to the surface of the tube and form an air flow path along the horizontal direction together with the tube are alternately stacked. A heat exchanger that performs heat exchange between the refrigerant flowing through the refrigerant flow path and the air flowing through the air flow path,
At the end on the downstream side in the air flow direction on the surface of the tube, a groove is formed along the vertical direction,
By positioning the downstream end of the corrugated fin in the air flow direction downstream of the end of the groove in the air flow direction, the end of the corrugated fin folded portion on the downstream side of the air flow direction. The heat exchanger is configured such that the condensed water accumulated at the end is drawn by the condensed water flowing downward through the groove, enters the groove, flows downward together with the condensed water, and is drained. The heat exchanger according to claim 1,
The corrugated fin has a plurality of convex portions on the downstream side in the air flow direction, and the width of the corrugated fin in the air flow direction including the width of the air flow direction of the convex portions is defined as the air flow of the tube. A heat exchanger characterized by matching the width of the direction. The heat exchanger according to claim 1,
The corrugated fin has an air flow direction downstream end and an air flow direction upstream end, each of which has a plurality of convex portions, and the air flow direction of the corrugated fin includes the width of the convex portions on both sides including the width in the air flow direction. The heat exchanger is characterized in that the width in the direction is made to coincide with the width in the air circulation direction of the tube. The heat exchanger according to claim 2 or 3,
The heat exchanger according to claim 1, wherein the convex portion is provided only on a flat portion of the corrugated fin. A flat tube in which a refrigerant flow path along the vertical direction is formed inside and corrugated fins that are joined to the surface of the tube and form an air flow path along the horizontal direction together with the tube are alternately stacked. A heat exchanger that performs heat exchange between the refrigerant flowing through the refrigerant flow path and the air flowing through the air flow path,
At the end of the tube surface on the downstream side in the air flow direction, a groove along the vertical direction is formed,
The upper end portion or the lower end portion or the upper end portion and the lower end portion of the tube are joined to the tank by brazing, and the upper end position, the lower end position, or the upper end position of the groove at the brazed joint portion between the tube and the tank, and A heat exchanger characterized in that a lower end position is separated from a tip position of the braze fillet. The heat exchanger according to claim 1, 2, 3 or 4,
The upper end portion or the lower end portion or the upper end portion and the lower end portion of the tube are joined to the tank by brazing, and the upper end position, the lower end position, or the upper end position of the groove at the brazed joint portion between the tube and the tank, and A heat exchanger characterized in that a lower end position is separated from a tip position of the braze fillet. The heat exchanger according to claim 5 or 6,
The heat exchanger according to claim 1, wherein a formation range of the groove is made to coincide with a range of joining lengths of the corrugated fins.

Images