JP2010025476A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger of an air conditioner capable of reducing ventilation resistance with excellent heat transfer performance even when dew condensation water adheres thereto. <P>SOLUTION: A first fin 71 is positioned between at least a first flat heat transfer tube 51 and a second flat heat transfer tube 52, has a plate-like part arranged to make its thickness direction orthogonal to an air flowing direction, and contacts at least either the first flat heat transfer tube 51 or the second flat heat transfer tube 52. The plate-like part is formed with a guide part S for guiding the dew condensation water which is generated on its surface to the downstream side by using an air flow. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an air-cooled and forced ventilation heat exchanger used in an air conditioner.

  As the heat exchanger of the air conditioner, for example, a plurality of heat transfer tubes extending in the horizontal direction are arranged in the vertical direction, and so-called laminated heat exchangers in which fins are arranged between the heat transfer tubes. Is used.

  As such a laminated heat exchanger, for example, as shown in Patent Document 1 below, a flat heat transfer tube extending in the horizontal direction and a surface extending perpendicularly to the direction in which the flat heat transfer tube extends are spread. The thing which has the fin penetrated by the cage | basket flat heat exchanger tube is proposed. According to the heat exchanger of Patent Literature 1, the flat surface of the flat heat transfer tube is inclined from the horizontal direction while the direction intersecting the extending direction of the flat heat transfer tube is the air flow direction, and the leeward side is positioned below the leeward side. It is arranged to do. And the fin is provided with the corrugated undulation part in order to improve heat-transfer performance, and the ridgeline of the undulation part is extended in the perpendicular direction.

In this heat exchanger, when the heat exchanger functions as a refrigerant evaporator, moisture contained in the ambient air becomes condensed water on the fin surface and may accumulate on the upper surface of the flat heat transfer tube. Even in that case, since the flat heat transfer tube is inclined so that the leeward side is downward, drainage of condensed water can be promoted. As a result, the air resistance passing through the heat exchanger can be reduced and the heat exchange efficiency can be improved when the drainage is promoted, compared with the case where condensed water stays on the flat heat transfer tube. is made of.
JP-A-2005-121318

  However, in the heat exchanger described in Patent Document 1 described above, when condensed water is generated on the surface of the fins, the condensed water tends to gather at the peak portion or valley portion of the ridge line of the undulating portion. And since the ridgeline of this undulation part is extended in the perpendicular direction, the condensed water which gathered is easy to flow down vertically downward by this weight along this ridgeline.

  Here, in the heat exchanger described in Patent Document 1, since the ridge line of the undulating portion and the air flow direction are provided so as to be orthogonal, the condensed water collected on the ridge line may receive an air flow. It is easy to move only vertically downward, and difficult to move in the leeward direction. Condensed water that collects in the ridges that form the valleys of the undulations is particularly difficult to move in the leeward direction.

  For this reason, even if the condensed water collected on the fins is subjected to an air flow, it cannot be kept small by moving according to the flow direction. Will increase.

  When the ventilation resistance increases in this way, the heat exchange efficiency in the heat exchanger is reduced as a result.

  The subject of this invention is providing the heat exchanger of the air conditioning apparatus which can reduce ventilation resistance even if it is a case where condensed water adheres, and has favorable heat transfer performance.

  A heat exchanger according to a first aspect of the present invention is an air-cooled and forced-air ventilation heat exchanger used in an air conditioner, and includes a first flat heat transfer tube, a second flat heat transfer tube, and a first fin. . The first flat heat transfer tube has a flat surface extending in a horizontal plane parallel to the air flow direction generated in the horizontal direction by forced ventilation, and in a horizontal direction orthogonal to the air flow direction. Pour refrigerant. The second flat heat transfer tube is disposed vertically below the first flat heat transfer tube, has a flat surface extending in a horizontal plane parallel to the air flow direction, and the refrigerant flow of the first flat heat transfer tube Let the coolant flow in a direction parallel to the direction. The first fin is located at least between the first flat heat transfer tube and the second flat heat transfer tube, has a plate-like portion arranged so that the thickness direction is orthogonal to the air flow direction, and the first flat It is in contact with at least one of the heat transfer tube and the second flat heat transfer tube. The plate-like portion is formed with a guide portion for guiding the condensed water generated on the surface to the downstream side using an air flow. Here, the horizontal is not limited to the exact horizontal, but includes a case where it is slightly inclined from the horizontal direction. Further, the vertical is not limited to the exact vertical, but includes a case where it is slightly inclined from the vertical direction. The guide shape includes, for example, a portion where the surface area of the fin is partially increased and the surface tension is stronger than that of the peripheral region, such as a slit or a protrusion.

  In this heat exchanger, since both the first flat heat transfer tube and the second flat heat transfer tube have a flat flat surface extending horizontally, compared to the case where they are inclined from the horizontal direction, Ventilation resistance against the flowing air can be kept small. Since the plate-like portion of the first fin is arranged so that the thickness direction thereof is orthogonal to the air flow direction, the ventilation resistance due to this plate-like portion can be suppressed to a small value. Since the first fin is in contact with at least one of the first flat heat transfer tube and the second flat heat transfer tube, the heat transfer area effective for heat exchange can be expanded. The plate-like part is formed with a guide for guiding the condensed water generated on the surface to the downstream side by using the air flow, so that moisture in the air is cooled by heat exchange, and condensation is formed on the plate-like member. Even if water is generated, the dew condensation water can be guided to the downstream side by the guide portion and the air flow, and drainage can be promoted. Thereby, the ventilation resistance of a heat exchanger by dew condensation water adhering to the surface of a plate-shaped member can be restrained small by encouraging drainage of this dew condensation water. Furthermore, since the guide part is formed on the plate-like member, the surface area is increased as compared with the case where nothing is formed, and the heat transfer performance can be improved.

  As described above, it is possible to perform efficient heat exchange by reducing the ventilation resistance while improving the heat transfer performance.

  A heat exchanger according to a second aspect is the heat exchanger according to the first aspect, wherein the guide portion is inclined so as to incline from the upstream side toward the downstream side in the air flow direction from the upper end portion toward the lower end portion. It has a shape.

  In this heat exchanger, the inclined shape of the guide portion is inclined from the upstream side toward the downstream side in the air flow direction from the upper end portion toward the lower end portion. For this reason, even if the air flow is supplied in a state where the dew condensation water is held by the guide part, the dew condensation water stays at the spot and does not increase the ventilation resistance, and the lower end part extends along the guide part. It can flow toward the side and increase in ventilation resistance can be suppressed to a small level.

  The heat exchanger according to a third aspect of the present invention is the heat exchanger according to the second aspect, wherein the plate-like portion is formed with only inclined shapes provided at a plurality of locations so as to be arranged in parallel to each other.

  In this heat exchanger, only the inclined shape that promotes drainage of the dew condensation water on the downstream side is provided at a plurality of locations on the plate-like member, so that the dew condensation water can be guided further downstream by the air flow. Become.

  The heat exchanger according to a fourth aspect is the heat exchanger according to the first aspect, wherein the guide portion has a water guide shape formed so as to extend from the upper end portion to the lower end portion while maintaining a position in the air flow direction. Are provided at a plurality of locations so as to be arranged in parallel with each other from the upstream side to the downstream side. The plurality of water guide shapes are arranged so that the height position of the lower end portion gradually decreases from the upstream side to the downstream side in the air flow direction.

  In this heat exchanger, the dew condensation water generated on the upstream side is replenished by the guide portion provided on the upstream side, and is easily guided to the lower end portion of the guide portion. And since the lower end part of the upstream guide part is arrange | positioned above the lower end part of the more downstream guide part, the dew condensation water collected on the lower end part of the upstream guide part is 2nd flat transmission. It exists in the position away from the heat pipe, and ventilation resistance is small compared with the 2nd flat heat exchanger tube upper surface vicinity. Thereby, the dew condensation water collected at the lower end of the upstream guide portion is easily guided to the downstream side by a relatively strong air flow. The condensed water guided to the downstream side is caught by the vicinity of the lower end of the downstream guide portion, and the condensed water is collected in the vicinity of the lower end portion of the downstream guide portion. Further, the condensed water can be guided to the downstream side by a relatively strong air flow to the downstream guide portion, and the condensed water can be effectively drained from the downstream end of the fin.

  The heat exchanger according to a fifth aspect of the present invention is the heat exchanger according to the first aspect, wherein the guide portion is formed so as to extend from the upper end portion to the lower end portion while maintaining the position in the air flow direction. Are provided at a plurality of locations so as to be arranged in parallel with each other from the upstream side to the downstream side. The plurality of water guide shapes are arranged so that the distance between adjacent water guide shapes gradually decreases from the upstream side to the downstream side in the air flow direction.

  In this heat exchanger, it is necessary that the downstream guide portion drains both the condensed water guided from the upstream side and the condensed water generated on the downstream side. On the other hand, here, in the region where the amount of condensed water on the upstream side is relatively small and the water droplets are relatively small, the guide portion is roughly arranged, so that when the condensed water adheres by providing many guide portions unnecessarily. The problem of increased draft resistance is avoided. In addition, in the area where the water droplets that collect a relatively large amount of condensed water on the downstream side are relatively large, the guides are densely arranged to replenish the condensed water and condense to the vicinity of the lower end of the guide part where the air flow is weak. Before the water is introduced, the empty flow can be applied at a height where the air flow is as strong as possible, and drainage is promoted.

  Thereby, it becomes possible to drain dew condensation water effectively from the downstream end of the fin.

  The heat exchanger according to a sixth aspect of the present invention is the heat exchanger according to any one of the second to fifth aspects of the present invention, wherein the water guide shape is a slit shape in which the plate-like portion is penetrated in the plate thickness direction or the plate-like portion. Is one of the projecting shapes that project in the thickness direction.

  In this heat exchanger, since the surface area is partially increased in the portion where the slit and the protruding shape are provided, the surface tension is likely to increase, and water is more easily guided to the intended place.

  A heat exchanger according to a seventh aspect is the heat exchanger according to the first aspect, wherein the guide portion is formed by cutting and raising the plate member so that the windward side in the air flow direction is a free end and the leeward side is a fixed end. The formed water guide shapes are provided at a plurality of locations so as to be arranged in parallel with each other from the upstream side to the downstream side in the air flow direction. The plurality of water guide shapes are provided with a cut shape whose width decreases in the vicinity of the lower end portion from the upstream side to the downstream side in the air flow direction.

  In this heat exchanger, the dew condensation water captured by the guide part tends to flow down to the lower end part of the guide part. The lower end portion of the guide portion is provided with a cut shape whose width becomes narrower from the upstream side to the downstream side of the air flow. For this reason, the dew condensation water led to the vicinity of the lower end portion of the guide portion is led further downstream by the surface tension of the cut-shaped portion.

  Thereby, compared with the case where it does not guide to the downstream side because there is no cut shape, the dew condensation water can be effectively guided downstream.

  The heat exchanger according to an eighth aspect of the present invention is the heat exchanger according to any one of the first to seventh aspects, further comprising a third flat heat transfer tube and a second fin. The third flat heat transfer tube is arranged vertically below the second flat heat transfer tube, has a flat surface extending in a horizontal plane parallel to the air flow direction, and the refrigerant flow of the second flat heat transfer tube Let the coolant flow in a direction parallel to the direction. The second fin is located at least between the second flat heat transfer tube and the third flat heat transfer tube and has a plate-like portion disposed so that the thickness direction is orthogonal to the air flow direction. It is in contact with at least one of the heat tube and the third flat heat transfer tube. The first fin and the second fin are separated from each other by the second flat heat transfer tube, and are independent from each other.

  In this heat exchanger, the second fin is formed on the upper layer of the third flat heat transfer tube, the second flat heat transfer tube is formed on the upper layer of the second fin, the first fin is formed on the upper layer of the second flat heat transfer tube, and the upper layer of the first fin. In addition, the first flat heat transfer tubes can be respectively stacked and arranged, and the interval between the flat heat transfer tubes can be easily secured by the intervening fins, and the assembly workability of the heat exchanger is improved.

  The heat exchanger of the ninth invention is the heat exchanger of the eighth invention, wherein the first fin and the second fin are corrugated fins arranged so as to have a wave shape when viewed from the air flow direction. .

  In this heat exchanger, since the heat transfer area is increased by using the waveform, efficient heat exchange can be performed.

  A heat exchanger according to a tenth aspect of the present invention is the heat exchanger according to any one of the first to seventh aspects, further comprising a third flat heat transfer tube and a second fin. The third flat heat transfer tube is arranged vertically below the second flat heat transfer tube, has a flat surface extending in a horizontal plane parallel to the air flow direction, and the refrigerant flow of the second flat heat transfer tube Let the coolant flow in a direction parallel to the direction. The second fin is located between the second flat heat transfer tube and the third flat heat transfer tube and has a plate-like portion disposed so that the thickness direction is orthogonal to the air flow direction, and the second flat heat transfer tube And at least one of the third flat heat transfer tubes. The first fin and the second fin are continuous with each other.

  In this heat exchanger, it is possible to easily assemble the heat exchanger by passing the first flat heat transfer tube and the second flat heat transfer tube through the first fin and the second fin from the thickness direction. .

  In the first invention, it is possible to perform efficient heat exchange by reducing the ventilation resistance while improving the heat transfer performance.

  In the second aspect of the invention, the increase in ventilation resistance can be kept small.

  In the third aspect of the invention, the dew condensation water can be guided further downstream by the air flow.

  In the fourth aspect of the invention, it is possible to effectively drain the dew condensation water from the downstream end of the fin.

  In the fifth aspect of the invention, it becomes possible to drain the condensed water from the downstream end of the fin effectively.

  In 6th invention, it is easy to guide water to the intended place more reliably.

  In the seventh aspect of the invention, compared to the case where it is not led to the downstream side due to the lack of the cut shape, the dew condensation water can be led effectively to the downstream side.

  In the eighth invention, the assembly workability of the heat exchanger is improved.

  In the ninth invention, efficient heat exchange can be performed.

  In the tenth aspect, the heat exchanger can be easily assembled.

<1> About the air conditioner in which the heat exchanger of the present invention is used The heat exchanger of the present invention can be used as at least a refrigerant evaporator in the air conditioner. When used in an air conditioner capable of switching between cooling operation and heating operation, the heat exchanger of the present invention can function not only as a refrigerant evaporator but also as a refrigerant radiator. It may be possible.

  The heat exchanger of the present invention is an air-cooled and forced air-flow heat exchanger. For this reason, the air conditioner is equipped with a blower (not shown) for supplying an air flow to the heat exchanger of the present invention.

  Here, the blower may be arranged on the downstream side of the heat exchanger or may be arranged on the upstream side with respect to the air flow direction generated by itself. Further, the air flow formed by the blower can be freely changed in the direction of the air flow direction by another member or the like that forms the blower flow path. Here, after changing the direction freely as described above, when passing through the heat exchanger, the heat exchanger is disposed so as to pass in a substantially horizontal direction.

  And when the heat exchanger of this invention is functioning as the refrigerant | coolant evaporator in an air conditioning apparatus, in the state in which air is supplied from a fan, a heat exchanger utilizes the air supplied by a fan. Heat exchange takes place. In the heat exchange here, the refrigerant flowing inside the heat transfer tubes is warmed and evaporated by the heat of the air supplied by the blower. On the other hand, the air supplied to the heat exchanger and passed through the heat exchanger is cooled by the heat of the refrigerant flowing inside the heat transfer tube, and the temperature is lowered. At this time, since the surface temperature of the heat exchanger is lower than the temperature of the supplied air, condensed water may be generated on the surface of the heat exchanger when the supplied air is cooled. is there.

  The heat exchanger of the present invention provides a heat exchanger having a structure that promotes drainage of water adhering to the surface of a heat exchanger such as condensed water.

  Hereinafter, a heat exchanger according to an embodiment of the present invention will be described with reference to the drawings.

<2> Heat exchanger (Overall configuration)
In FIG. 1, the external appearance perspective view of the heat exchanger 1 is shown. In FIG. 1, detailed portions of fins 7 to be described later are omitted.

  As shown in FIG. 1, the side on which the heat exchanger 1 can be seen is the front side, and the back side, left side, right side, top side, and bottom side are grasped on the basis of the front side. ,explain.

  FIG. 2 shows a partially enlarged view of a portion indicated by A in FIG.

  FIG. 3 is a side sectional view showing details of the flat heat transfer tubes 5 and the fins 7 in the BB cross section in FIG. 2. In FIG. 3, portions of the fin 7 that are not located in the cross section are also shown for explanation.

  FIG. 4 shows a partially enlarged schematic perspective view of the heat exchanger 1.

  The heat exchanger 1 includes a diversion header 2, a merge header 3, flat heat transfer tubes 5, and fins 7.

  A liquid refrigerant or a gas-liquid two-phase refrigerant is fed into the diversion header 2 from the direction indicated by R1 in FIG. Then, the refrigerant supplied to the diversion header 2 flows to the merging header 3 by being divided into a plurality of flow paths of the flat heat transfer tubes 5.

  The merging header 3 is provided at the same position in the air flow direction component as the divergence header 2, and merges the refrigerants flowing from the plurality of flow paths of the flat heat transfer tube 5 in the direction indicated by R2 in FIG. Send out the refrigerant.

  As shown in FIGS. 3 and 4, the flat heat transfer tube 5 is formed of aluminum or an aluminum alloy, and is arranged in the vertical direction, the first flat heat transfer tube 51, the second flat heat transfer tube 52, and the third It has a flat heat transfer tube 53 and the like. The first flat heat transfer tube 51, the second flat heat transfer tube 52, the third flat heat transfer tube 53, and the like have flat surfaces that extend in the horizontal direction on the vertical upper side and the vertical lower side, respectively, and the longitudinal direction is the air flow. It extends in a direction perpendicular to the direction and in the horizontal direction. As described above, the flat heat transfer tube 5 has a flat flat surface horizontally spread, and therefore, the ventilation resistance to the air flow flowing in the horizontal direction is reduced compared to the case where the flat heat transfer tube 5 is inclined from the horizontal direction. Can do. The first flat heat transfer tube 51, the second flat heat transfer tube 52, the third flat heat transfer tube 53, and the like all flow refrigerant in the longitudinal direction, which is a direction orthogonal to the air flow direction, as shown in FIG. These heat transfer tubes are called so-called multi-hole tubes. The plurality of refrigerant flow paths P are provided side by side so as to be parallel to each other in the air flow direction in the heat transfer tube in order to form the heat transfer tube in a flat shape. Moreover, the pipe diameter of the refrigerant | coolant flow path P is very small, and one is a square shape of 250 micrometers x 250 micrometers, and is what is called a microchannel heat exchanger.

  As shown in the front views of FIGS. 2, 3, and 4, the fin 7 has a wave shape in which a peak portion and a valley portion are repeatedly formed in a front view, and is made of aluminum or an aluminum alloy. Between the first flat heat transfer tube 51, the second flat heat transfer tube 52, the third flat heat transfer tube 53, and the like, there are a first fin 71, a second fin 72, and the like arranged separately from each other. The fin 7 has a plate-like portion that spreads flatly from the peak portion to the valley portion. As shown in FIG. 3, each of the first fin 71 and the second fin has a guide portion S for guiding the condensed water to the downstream side in the air flow direction while increasing the heat transfer area. is doing. In addition, the plate | board thickness direction of the fin 7 is provided so that it may become a direction orthogonal to an air flow direction. Thereby, the ventilation resistance by providing the fin 7 can be suppressed small. Moreover, the thickness of the fin 7 is 0.1 mm. The fins 7 are not provided with irregularities in the thickness direction other than the guide portions S.

  As shown in FIG. 2, the first fin 71 is disposed so as to be sandwiched between the first flat heat transfer tube 51 and the second flat heat transfer tube 52, and is formed on the flat surface on the lower surface side of the first flat heat transfer tube 51. On the other hand, the upper surface side of the mountain portion is in contact with the lower flat surface on the upper surface side of the second flat heat transfer tube 52, and the lower surface side of the valley portion is in contact therewith. Similarly, the second fin 71 is also arranged so as to be sandwiched between the second flat heat transfer tube 52 and the third flat heat transfer tube 53, and has a mountain portion with respect to the flat surface on the lower surface side of the second flat heat transfer tube 52. The upper surface side is in contact with the lower flat surface on the upper surface side of the third flat heat transfer tube 53, and the lower surface side of the valley portion is in contact therewith. And the part which the flat heat exchanger tube 5 and the fin 7 are contacting in this way is being fixed by brazing welding. In this way, the first fin 71 and the second fin are fixed to the flat heat transfer tube 5, so that the heat flowing in the refrigerant flowing in the flat heat transfer tube 5 is transferred only to the surface of the flat heat transfer tube 5. In addition, heat can be transferred to the surface of the fin 7. Thereby, the heat transfer area of the heat exchanger 1 can be increased, the heat exchange efficiency can be improved, and the heat exchanger 1 itself can be made compact. The heat exchanger 1 is a so-called laminated heat exchanger in which flat heat transfer tubes 5 and fins 7 are alternately stacked in the vertical direction. Thus, since the heat exchanger 1 is a stacked heat exchanger, the second fin 72 is provided on the upper layer of the third flat heat transfer tube 53, and the second flat heat transfer tube 52 is provided on the upper layer of the second fin 72. In addition, the first fin 71 and the first flat heat transfer pipe 51 can be stacked on the upper layer of the second flat heat transfer tube 52 and the upper layer of the first fin 71, respectively. Therefore, the heat exchanger can be easily assembled and workability of the heat exchanger can be improved.

(Refrigerant flow)
A mode in which the refrigerant flows into the heat exchanger 1 having the above configuration and the refrigerant flows out of the heat exchanger 1 will be described.

  First, a liquid refrigerant or a gas-liquid two-phase refrigerant flows into the diversion header 2, and each refrigerant flow path P such as each first flat heat transfer tube 51, second flat heat transfer tube 52, and third flat heat transfer tube 53 is provided. Are divided evenly.

  While flowing through each refrigerant flow path P such as the first flat heat transfer tube 51, the second flat heat transfer tube 52, and the third flat heat transfer tube 53, the fins 7 and the flat heat transfer tubes 5 themselves are warmed by the air supplied by the blower. Thus, the refrigerant flowing inside is also warmed. As heat is applied to the refrigerant in this manner, the refrigerant gradually evaporates into a gas phase state in the process of passing through the refrigerant flow path P. In this process, the surface of the heat exchanger 1 is in a state where moisture in the air cooled by the heat of the refrigerant is attached as condensed water.

  And the refrigerant | coolant which became a substantially gaseous phase state passes through each refrigerant | coolant flow paths P, such as the 2nd flat heat exchanger tube 52 and the 3rd flat heat exchanger tube 53, Then, it merges by the merge header 3, and becomes one refrigerant flow. And flows out of the heat exchanger 1.

(Fin guide S)
As shown in FIG. 3, the first fin 71 and the second fin 72 of the fin 7 are guide portions S for guiding condensed water generated on the surfaces of the fin 7 and the flat heat transfer tube 5 to the downstream side in the air flow direction. have.

  As shown in FIG. 3, the guide portion S has slits that are inclined so as to extend gradually downward from the upstream side to the downstream side, and are arranged in parallel to each other in the air flow direction. Arranged and configured. This slit is a cut provided so as to penetrate the fin 7 in the plate thickness direction, and has a width of about 0.05 mm.

(Condensate drainage)
As described above, when the heat exchanger 1 functions as a refrigerant evaporator, condensed water is generated on the surface of the heat exchanger 1. And since this dew condensation water increases the ventilation resistance of the heat exchanger 1, if it retains on the surface of the heat exchanger 1, heat exchange efficiency will not be able to be kept favorable.

  In contrast, in the fin 7 of the heat exchanger 1 of the present embodiment, the guide portion S provided with a plurality of slits that are inclined so as to be positioned downward from the upstream side to the downstream side in the air flow direction. Is provided. For this reason, as shown in FIG. 5, the dew condensation adhering to the plate-shaped part of the fin 7 is easy to be guide | induced to the downstream of the air flow direction. For this reason, the dew condensation water generated in the heat exchanger 1 does not stay on the surface of the heat exchanger 1 and is easily guided to the downstream side by the air flow F and the guide portion S. The ventilation resistance of 1 can be suppressed small.

<3> Features of Heat Exchanger of Present Embodiment A conventional heat exchanger 901 includes, for example, flat heat transfer tubes 951, 952, and 953 having a refrigerant flow path P, and flat heat transfer tubes 951 as shown in FIG. , 952 and 953, fins 971 and 972. The fins 971 and 972 are provided with a slit S9 extending in the vertical direction. In this conventional heat exchanger 901, even if the condensed water generated on the surface of the heat exchanger 901 adheres to the fins 971 and 972, even if the slit 9S holds the condensed water and the air flow is supplied, The condensed water stays at the same position in the air flow direction, and the ventilation resistance is increased.

  On the other hand, in the heat exchanger 1 of the present embodiment, in the fin 7, a guide portion S is provided in which a plurality of slits are provided which are positioned downward from the upstream side to the downstream side in the air flow direction. Has been. For this reason, the dew condensation water generated on the surfaces of the flat heat transfer tubes 5 and the fins 7 of the heat exchanger 1 and dripping down to the vicinity of the slit S or the dew condensation water generated in the vicinity of the slit S receives the air flow F. Therefore, the air does not stay in the same place in the air flow direction, but is more easily guided to the downstream side while flowing down.

  Thereby, the ventilation resistance by dew condensation water staying on the fin 7 can be suppressed small. In addition, as described above, the dew condensation water is sent to the downstream side by the air flow F, so that drainage from the heat exchanger 1 can be promoted. For this reason, the dew condensation water stagnating in the heat exchanger 1 can be reduced, the ventilation resistance can be kept small, and the heat exchange efficiency can be improved.

<4> Modifications In the above embodiment, one embodiment of the present invention has been described as an example. However, the present invention is not limited to this, and various modifications as described below are possible without departing from the scope of the invention.

(A)
In the heat exchanger 1 of the said embodiment, the case where the slit of the guide part S was inclined and provided in the air flow direction downstream was demonstrated as an example.

  However, the present invention is not limited to this. For example, you may have guide part S2 like the heat exchanger 201 shown in FIG.

  Here, the flat heat transfer tubes 251 and 252 having the refrigerant flow path P sandwich the first fin 271 and the flat heat transfer tubes 252 and 253 having the refrigerant flow path P sandwich the second fin 272. is there. Here, the guide part S2 provided in the fins 271 and 272 is configured by arranging slits extending in the vertical direction in parallel with the air flow direction, and the upper end of the slit is arranged downstream in the air flow direction. The slits are provided so that the upper ends of the slits are inclined and arranged toward the downstream side so that the slits are positioned below the slits arranged on the upstream side. Also, with respect to the lower end of the slit, the lower end of each slit is directed toward the downstream side so that the slit disposed on the downstream side in the air flow direction is positioned lower than the slit disposed on the more upstream side. It is provided so as to line up at an angle.

  In the heat exchanger 201 of the modified example A, as shown in FIG. 7, the dew condensation water generated on the upstream side is easily replenished by the element lit upstream of the guide portion S2, and is easily guided to the lower end portion of the slit. Since the lower end portion of the slit on the upstream side of the guide portion S2 is disposed above the lower end portion of the slit on the further downstream side of the guide portion S2, it accumulates on the lower end portion of the slit on the upstream side of the guide portion S2. The condensed water is present at a more information position away from the flat surface on the upper surface side of the second flat heat transfer tube 252, and is present at a position where the ventilation resistance is smaller than that near the upper surface of the second flat heat transfer tube 252. Will be. Thereby, the dew condensation water collected at the lower end on the upstream side of the guide part S2 is easily guided to the slit on the downstream side by a relatively strong air flow. And the dew condensation water led to the slit on the downstream side is caught by the vicinity of the lower end of the slit on the downstream side of the guide part S2, and collected near the lower end of the slit on the downstream side of the guide part S2. Further, the condensed water can be guided to the slit on the downstream side of the guide portion S2 by a relatively strong air flow, and the condensed water can be effectively drained from the downstream end of the fin 7.

(B)
In the heat exchanger 1 of the said embodiment, the case where the slit of the guide part S was inclined and provided in the air flow direction downstream was mentioned as an example, and was demonstrated.

  However, the present invention is not limited to this. For example, you may have guide part S3 like the heat exchanger 301 shown in FIG.

  Here, the flat heat transfer tubes 351, 352 having the refrigerant flow path P sandwich the first fin 371, and the flat heat transfer tubes 352, 353 having the refrigerant flow path P sandwich the second fin 372. is there. Here, the guide part S3 provided in the fins 371 and 372 is configured by arranging slits extending in the vertical direction in parallel with the air flow direction, and the interval between the closest slits is the air flow direction. It is provided so as to gradually become narrower toward the downstream side than the upstream side. That is, the slits on the upstream side are arranged roughly and the slits on the downstream side are arranged densely.

  In the heat exchanger 301 of the modified example B, as shown in FIG. 9, the condensed water generated on the upstream side is replenished by a slit provided on the upstream side of the guide part S3, but on the downstream side of the guide part s3. It is necessary to drain both the condensed water guided from the upstream side and the condensed water generated on the downstream side. Here, in the region where the amount of condensed water on the upstream side is relatively small and the water droplets are relatively small, the slits of the guide portion S3 are roughly arranged, so that a large amount of guide portions are provided unnecessarily, and the ventilation resistance when the condensed water adheres The problem of increasing is avoided. Further, in the region where the water droplets where a large amount of condensed water gathers on the downstream side are relatively large, the slits of the guide part S3 are densely arranged to replenish the condensed water and the slits of the guide part S3 having a weak air flow. Before the condensed water is guided to the vicinity of the lower end of the tube (near the surface of the flat heat transfer tube), the empty flow can be applied at a height position where the air flow is as strong as possible, and the drainage can be promoted. Thereby, dew condensation water can be effectively drained from the downstream end of fin 371,372.

(C)
In the heat exchanger 1 of the said embodiment, the case where the slit of the guide part S was inclined and provided in the air flow direction downstream was mentioned as an example, and was demonstrated.

  However, the present invention is not limited to this. For example, you may have guide part S4 like the heat exchanger 401 shown in FIG.

  Here, the flat heat transfer tubes 451 and 452 having the refrigerant flow path P sandwich the first fin 471, and the flat heat transfer tubes 452 and 453 having the refrigerant flow path P sandwich the second fin 472. is there. Here, the guide part S4 provided in the fins 471 and 472 is configured such that the cut and raised portions extending in the vertical direction are arranged in parallel to the air flow direction. As shown in FIG. 11, this cut and raised is formed such that the downstream side in the air flow direction is a fixed end, the upstream side is a free end, and condensed water is collected at the downstream fixed end. Further, the cut-and-raised portion has raised portions ZH and ZL whose upper and lower ends are raised in the air flow direction, and a cut-and-raised plane portion ZM connecting the raised portion ZH at the upper end and the raised portion ZL at the lower end. . Then, as shown in FIG. 13, the lower end side of the guide portion S <b> 4 is cut out so that the distance between the cut and raised portion and the peripheral portion of the cut and raised portion becomes narrower toward the downstream side in the air flow direction. A cut shape Z1 is formed.

  In the heat exchanger 401 of Modification C, as shown in FIG. 12, the dew condensation water captured by the guide S4 is likely to flow down to the lower end of the cut and raised. The lower end portion of the cut and raised portion is provided with a cut shape Z1 whose width becomes narrower from the upstream side to the downstream side of the air flow. For this reason, the dew condensation water led to the vicinity of the lower end of the cut and raised portion is led further downstream by the surface tension of the cut shape Z1 part. Thereby, compared with the case where it does not guide to the downstream side due to the absence of the cut shape Z1, the dew condensation water can be effectively guided to the downstream side, and the drainage effect can be improved.

  Note that the cut shape of the modified example C is not limited to this, and for example, as shown in FIG. 14, the cut-and-raised plane portion ZM and the lower-end raised portion ZL toward the downstream side in the air flow direction. A cut shape Z2 that is cut so that the distance between the first and second electrodes becomes narrow may be formed. Further, for example, as shown in FIG. 15, a cut shape Z3 is formed so that the distance between the raised portion ZL at the lower end and the peripheral portion of the cut and raised becomes narrower toward the downstream side in the air flow direction. May be.

(D)
In the above-described embodiment, the slit formed by cutting as an example of the guide portion S has been described as an example.

  However, the present invention is not limited to this, and for example, irregularities may be provided instead of the slits.

(E)
In the above-described embodiment, the case where the shape of the fin 7 is a wave shape has been described as an example.

  However, the present invention is not limited to this, and for example, the plate-like portion may be provided so as to extend in the vertical direction.

(F)
In the above-described embodiment, the laminated heat exchanger has been described as an example.

  However, the present invention is not limited to this. For example, in the above-described embodiment, the fin 7 that is discontinuous by the flat heat transfer tube 5 is provided with a portion that protrudes in the air flow direction from the flat heat transfer tube 5. It may be a cross fin tube type heat exchanger formed so as to be continuous.

  When the heat exchanger of the present invention is applied to a heat exchanger capable of functioning as a refrigerant evaporator in an air conditioner, it is possible to promote drainage of condensed water and suppress ventilation resistance. It is particularly useful.

It is a general | schematic external appearance perspective view of the heat exchanger of this embodiment. It is the elements on larger scale of the part shown by A in FIG. It is a cross-sectional view at the time of cut | disconnecting in the surface shown by BB in FIG. It is a schematic perspective view of a heat exchanger. It is a figure which shows a mode that condensed water is drained in a heat exchanger. It is a cross-sectional view of the heat exchanger concerning a modification (A). It is a figure which shows a mode that dew condensation water is drained in the heat exchanger concerning a modification (A). It is a cross-sectional view of the heat exchanger concerning a modification (B). It is a figure which shows a mode that dew condensation water is drained in the heat exchanger concerning a modification (B). It is a cross-sectional view of the heat exchanger concerning a modification (C). It is sectional drawing which shows the cut-and-raised shape of the heat exchanger concerning a modification (C). It is a figure which shows a mode that dew condensation water is drained in the heat exchanger concerning a modification (C). It is the elements on larger scale which show the cut | notch part of the heat exchanger concerning a modification (C). It is the elements on larger scale which show the other variation of the cut | notch part of the heat exchanger concerning a modification (C). It is the elements on larger scale which show the other variation of the cut | notch part of the heat exchanger concerning a modification (C). It is a cross-sectional view of a conventional laminated heat exchanger. It is the elements on larger scale which show the cut and raised shape of the conventional heat exchanger.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Shunt header 3 Merge header 5 Flat heat exchanger tube 7 Fin 51-53 1st flat heat exchanger tube-3rd flat heat exchanger tube 71-72 1st fin-2nd fin P Refrigerant flow path S Guide part

Claims (10)

An air-cooled and forced-air ventilation heat exchanger (1) used in an air conditioner,
A flat surface extending in a horizontal plane parallel to an air flow direction generated in the horizontal direction by the forced ventilation, and a first flow of the refrigerant in a horizontal direction perpendicular to the air flow direction. A flat heat transfer tube (51);
The first flat heat transfer tube is disposed vertically below, has a flat surface extending in a horizontal plane parallel to the air flow direction, and is parallel to the refrigerant flow direction of the first flat heat transfer tube. A second flat heat transfer tube (52) for flowing refrigerant in the direction;
At least a plate-like portion located between the first flat heat transfer tube and the second flat heat transfer tube and having a thickness direction orthogonal to the air flow direction; A first fin (71) in contact with at least one of the heat tube and the second flat heat transfer tube;
With
The plate-like portion is formed with a guide portion (S) for guiding the condensed water generated on the surface to the downstream side using the air flow.
Heat exchanger (1). The guide part (S) has an inclined shape formed so as to incline from the upstream side to the downstream side in the air flow direction as it goes from the upper end part to the lower end part.
The heat exchanger (1) according to claim 1. In the plate-like portion, only the inclined shape provided at a plurality of locations so as to be arranged in parallel to each other is formed,
The heat exchanger (1) according to claim 2. The guide portions (S) are arranged such that water guide shapes formed so as to extend from the upper end portion to the lower end portion while maintaining the position in the air flow direction are parallel to each other from the upstream side to the downstream side in the air flow direction. It is provided in multiple places so that
The plurality of water guide shapes are arranged such that the height position of the lower end portion gradually decreases from the upstream side to the downstream side in the air flow direction.
The heat exchanger (1) according to claim 1. The guide parts (S) are arranged such that water guide shapes formed so as to extend from the upper end part to the lower end part while maintaining the position in the air flow direction are arranged in parallel to each other from the upstream side to the downstream side in the air flow direction. It is provided in multiple places so that
The plurality of water guide shapes are arranged such that the distance between adjacent water guide shapes gradually decreases from the upstream side to the downstream side in the air flow direction.
The heat exchanger (1) according to claim 1. The water conveyance shape is either a slit shape that penetrates the plate-like portion in the plate thickness direction, or a protruding shape that protrudes the plate-like portion in the plate thickness direction.
The heat exchanger (1) according to any one of claims 2 to 5. The guide portion (S) has a water guide shape formed by cutting and raising the plate-like member so that the windward side in the airflow direction is a free end and the leeward side is a fixed end, and the guide portion (S) is upstream of the airflow direction. It is provided at multiple locations so as to be arranged parallel to each other from the side to the downstream side,
The plurality of water guide shapes are provided with a cut shape (Z1) whose width decreases in the vicinity of the lower end portion from the upstream side to the downstream side in the air flow direction.
The heat exchanger (1) according to claim 1. The second flat heat transfer tube is disposed vertically below, has a flat surface extending in a horizontal plane parallel to the air flow direction, and is parallel to the refrigerant flow direction of the second flat heat transfer tube. A third flat heat transfer tube (53) for flowing refrigerant in the direction;
At least a plate-like portion positioned between the second flat heat transfer tube and the third flat heat transfer tube and having a thickness direction orthogonal to the air flow direction; and the second flat heat transfer tube And a second fin (72) in contact with at least one of the third flat heat transfer tube,
Further comprising
The first fin (71) and the second fin (72) are separated without being continuous with each other by being partitioned by the second flat heat transfer tube (52).
The heat exchanger (1) according to any one of claims 1 to 7. The first fin (71) and the second fin (72) are corrugated fins arranged so as to have a wave shape when viewed from the air flow direction.
The heat exchanger (1) according to claim 8. The second flat heat transfer tube is disposed vertically below, has a flat surface extending in a horizontal plane parallel to the air flow direction, and is parallel to the refrigerant flow direction of the second flat heat transfer tube. A third flat heat transfer tube (53) for flowing refrigerant in the direction;
A plate-like portion located between the second flat heat transfer tube (52) and the third flat heat transfer tube (53) and disposed so that the thickness direction is perpendicular to the air flow direction; A second fin (72) in contact with at least one of the second flat heat transfer tube and the third flat heat transfer tube;
Further comprising
The first fin (71) and the second fin (72) are continuous with each other.
The heat exchanger (1) according to any one of claims 1 to 7.

Images