JP5246322B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger.

  A heat exchanger for heating or cooling air is used in an outdoor unit of an air conditioner, a heat source unit of a hot water supply device, or the like. As a kind of heat exchanger, there exists a thing shown by patent document 1 (Unexamined-Japanese-Patent No. 2008-101847), for example.

  In the heat exchanger of Patent Document 1, the heat transfer tube is arranged so that the flat portion of the flat heat transfer tube is horizontal, and corrugated fins are arranged between the flat heat transfer tubes positioned apart from each other. It has a structure. In particular, the heat exchanger of Patent Document 1 has a structure having a protruding portion that extends from the heat transfer surface of the corrugated fin and protrudes from the flat portion of the flat heat transfer tube, and the protruding portion is the condensed water of the corrugated fin. Functions as a water surface. Thereby, condensed water flows below through the said water conveyance surface.

  Since the corrugated fin according to Patent Document 1 has a structure bent into a corrugated shape, a plurality of plate-shaped heat transfer surfaces adjacent to each other in the plate thickness direction, the above-described water transfer surfaces, and heat transfer surfaces adjacent to each other. And a bent portion to be joined. As a material for the corrugated fin, a so-called clad material having a brazing material applied on the surface is often used, and the corrugated fin and the flat heat transfer tube are joined by brazing.

  However, depending on the area of the water transfer surface extending from each adjacent heat transfer surface, the corrugated fin and the flat heat transfer tube may not be in sufficient contact due to the difference in the amount of brazing material, or the brazing material may be melted unnecessarily. So-called erosion may occur.

  Then, the subject of this invention is making a fin and a heat exchanger tube contact without a problem, ensuring the water conveyance function of condensed water.

  The heat exchanger according to the first aspect of the present invention includes fins and a plurality of heat transfer tubes. The fin has a plate-like first fin portion and second fin portion. The first fin portion and the second fin portion are arranged such that the plate thickness direction intersects the air flow direction, and are adjacent to each other. The plurality of heat transfer tubes are inserted into the fins so as to intersect the air flow direction. And the 1st fin part and the 2nd fin part have a heat-transfer part, an upper water guide part, and a lower water guide part. The heat transfer unit exchanges heat with air. The upper water guide part protrudes upward from the heat transfer part. The lower water guide portion protrudes downward from the heat transfer portion. The amount of protrusion of the upper water guide portion of the first fin portion is different from the amount of protrusion of the upper water guide portion of the second fin portion, but is equal to the amount of protrusion of the lower water guide portion of the second fin portion. The amount of protrusion of the lower water guide portion of the first fin portion is different from the amount of protrusion of the lower water guide portion of the second fin portion, but is equal to the amount of protrusion of the upper water guide portion of the second fin portion.

  According to this heat exchanger, the first fin portion and the second fin portion that are adjacent to each other have different amounts of protrusion of the upper water guide portion and different amounts of protrusion of the lower water guide portion. And the protrusion amount of the upper water conveyance part of a 1st fin part is equal to the protrusion amount of the lower water conveyance part of a 2nd fin part, and the protrusion amount of the lower water conveyance part of a 1st fin part is the upper water conveyance part of a 2nd fin part. Is equal to the amount of protrusion. Therefore, the sum of the areas of the upper water guide portion and the lower water guide portion in the first fin portion is equal to the sum of the areas of the upper water guide portion and the lower water guide portion in the second fin portion. Therefore, it is possible to prevent the fins and the heat transfer tubes from being in sufficient contact due to the difference in the amount of brazing material, or so-called erosion that unnecessarily melts the brazing material. Therefore, the fin and the heat transfer tube can be brought into contact with each other without any problem while ensuring the function of guiding the condensed water.

  The heat exchanger which concerns on the 2nd viewpoint of this invention is a heat exchanger which concerns on a 1st viewpoint, Comprising: A 1st fin part and a 2nd fin part are the centerline which divides the width | variety along an air flow direction into 2 equal parts On the other hand, it has a symmetrical shape.

  Thereby, the sum total of the area of the upper water conveyance part and lower water conveyance part in a 1st fin part and the sum total of the area of the upper water conveyance part and lower water conveyance part in a 2nd fin part become equal. Therefore, it is possible to further prevent a difference in the amount of brazing material between the first fin portion and the second fin portion.

  The heat exchanger which concerns on the 3rd viewpoint of this invention is a heat exchanger which concerns on a 1st viewpoint or a 2nd viewpoint, Comprising: An upper water conveyance part and a lower water conveyance part are the shapes which become narrow toward the front-end | tip part. Have.

  Thereby, the part which contacts a heat exchanger tube is ensured in a fin, and also it becomes easy to ensure the water conveyance function of condensed water.

  A heat exchanger according to a fourth aspect of the present invention is the heat exchanger according to any one of the first to third aspects, wherein the fin is between the adjacent heat transfer tubes and the plate-like member is about 90 degrees. It is formed by being bent into corrugations one by one.

  As a result, even when so-called corrugated fins are used as the fins, the fins and the heat transfer tubes may not be in sufficient contact due to the difference in the amount of brazing material, or so-called erosion may occur that unnecessarily melts the brazing material. Can be prevented.

  According to the heat exchanger which concerns on the 1st viewpoint of this invention, a fin and a heat exchanger tube can be contacted without a problem, ensuring the water conveyance function of condensed water.

  According to the heat exchanger according to the second aspect of the present invention, it is possible to further prevent a difference in the amount of brazing material between the first fin portion and the second fin portion.

  According to the heat exchanger which concerns on the 3rd viewpoint of this invention, the part which contacts a heat exchanger tube is ensured to a fin, and also the water conveyance function of condensed water becomes easy to be ensured.

  According to the heat exchanger according to the fourth aspect of the present invention, the fin and the heat transfer tube do not sufficiently contact each other due to the difference in the amount of brazing material, or so-called erosion that unnecessarily melts the brazing material occurs. Can be prevented.

The external view of the heat exchanger which concerns on this embodiment. The enlarged view of the part shown by A in FIG. The schematic perspective view of the heat exchanger which concerns on this embodiment. It is a cross section at the time of cut | disconnecting in the surface shown by IV-IV in FIG. 2, Comprising: The side view at the time of seeing the heat exchanger of FIG. 3 from the right side. The figure for demonstrating the fin formed from one plate-shaped member. The external view of the 1st fin part which concerns on this embodiment. The external view of the 2nd fin part which concerns on this embodiment. FIG. 6 is an external view of a fin formed by bending the plate-like member of FIG. 5 into a corrugated shape. The figure at the time of seeing the fin and flat heat exchanger tube which were mutually joined from the air flow direction. The external view of the conventional 1st fin part. The external view of the conventional 2nd fin part. The cross-sectional view of a fin at the time of cut | disconnecting in the surface shown by XII-XII in FIG.

  Hereinafter, the heat exchanger according to the present invention will be described in detail with reference to the drawings. The following embodiments are specific examples of the present invention and do not limit the technical scope of the present invention.

(1) Outline FIG. 1 is an external view of a heat exchanger 10 according to an embodiment of the present invention. The heat exchanger 10 according to the present embodiment is provided inside an outdoor unit of the air conditioner, and can function as a refrigerant evaporator or a refrigerant radiator.

  Although not shown in the drawings, in this embodiment, the air conditioner is an example of a separate type configured by being divided into an outdoor unit installed outdoors and an indoor unit installed indoors. take. Examples of the operation type of the air conditioner include a cooling operation and a heating operation, and a defrost operation for removing frost attached to the heat exchanger 10 in the outdoor unit.

  The heat exchanger 10 according to the present embodiment is an air-cooled and ventilated heat exchanger. For this reason, the air conditioner is provided with a blower (not shown) that supplies an air flow to the heat exchanger 10. Hereinafter, the air flow direction is indicated as “F” in the drawings.

  Here, the air blower may be disposed on the downstream side of the heat exchanger 10 or on the upstream side with respect to the air flow direction F generated by itself. Moreover, the air flow direction F can be freely changed by the other member etc. which form a ventilation flow path. When the air whose direction has been freely changed passes through the heat exchanger 10, the heat exchanger is arranged so that the air passes in a substantially horizontal direction.

  In the state where the air from the blower is supplied to the heat exchanger 10 functioning as the refrigerant evaporator, the heat exchanger 10 performs heat exchange using the air supplied by the blower. In the heat exchange between the refrigerant and the air in this case, the refrigerant flowing in the flat heat transfer tubes 41, 42, 43,... Described later is heated and evaporated by the heat of the air supplied by the blower. To do. On the other hand, since the air which passed the heat exchanger 10 is cooled by the heat | fever of the refrigerant | coolant which flows through the inside of the flat heat exchanger tubes 41, 42, 43, ..., the temperature of air falls. At this time, since the surface temperature of the heat exchanger 10 is lower than the temperature of the supplied air, when the supplied air is cooled, moisture in the air is cooled and heat exchange is performed. May adhere to the surface of the vessel 10 as condensed water.

  Therefore, the heat exchanger 10 according to the present embodiment has a structure that guides the condensed water downward.

(2) Structure of heat exchanger Next, the structure of the heat exchanger 10 which concerns on this embodiment is explained in full detail. As shown in FIG. 1, the heat exchanger 10 mainly includes a diversion header 20, a merge header 30, a flat heat transfer tube group 40, and a fin group 50.

  In the following description, expressions indicating directions such as “up”, “down”, “vertical”, and “horizontal” are used as appropriate, but these are states in which the heat exchanger 10 is installed in the state of FIG. Represents each direction at. Further, as shown in FIG. 1, the side on which the heat exchanger 10 can be viewed is referred to as “front side”, and “upper surface side” and “lower surface side” are grasped on the basis of the front side.

(2-1) Shunt header and merge header As shown in FIG. 1, the longitudinal direction of the shunt header 20 and the merge header 30 are both vertical. A flat heat transfer tube group 40 is connected to the diversion header 20 and the merge header 30. Specifically, the diversion header 20 and the merge header 30 extend in parallel at a predetermined distance from each other, and the flat heat transfer tubes 41, 42, 43... In the flat heat transfer tube group 40 along the longitudinal direction thereof. They are connected in an array.

  A liquid state refrigerant or a gas-liquid two-phase state refrigerant is fed into the diversion header 20 from the direction R1 in FIG. The refrigerant supplied to the diversion header 20 flows to the merging header 30 by being divided into a plurality of flow paths of the flat heat transfer tubes 41, 42, 43,.

  The merging header 30 is provided at the same position as the diversion header 20 in the component in the air flow direction F, and the refrigerant has flowed from the plurality of flow paths of the plurality of flat heat transfer tubes 41, 42, 43,. And the refrigerant is sent out in the direction R2 in FIG.

(2-2) Flat Heat Transfer Tube Group As shown in FIGS. 3, 4, and 9, the flat heat transfer tube group 40 includes a plurality of flat heat transfer tubes (corresponding to heat transfer tubes) 41, 42, 43,. ing.

  The flat heat transfer tubes 41, 42, 43,... Are formed of aluminum or an aluminum alloy, and are formed on the fin group 50 so as to intersect (specifically, substantially perpendicular) to the air flow direction F generated by ventilation. Has been inserted. More specifically, the flat heat transfer tubes 41, 42, 43,... Are arranged side by side at a predetermined distance in the vertical direction as shown in FIGS. , Flat surfaces 41a, 41b, 42a, 42b, 43a, 43b,... Spreading in a horizontal plane substantially parallel to the air flow direction F generated in the horizontal direction by ventilation. The flat surfaces 41a, 41b, 42a, 42b, 43a, 43b,... Spread horizontally in the vertical upper side and the vertical lower side. As described above, since the flat surfaces 41a, 41b, 42a, 42b, 43a, 43b, ... are spread horizontally, the flat heat transfer tubes 41, 42, 43, ... are inclined from the horizontal direction. Compared with the case where it arrange | positions, the ventilation resistance with respect to the air flow which is flowing along a horizontal direction can be restrained small.

  Each of the flat heat transfer tubes 41, 42, 43,... Has a plurality of refrigerant flow paths P that allow the refrigerant to flow in a direction substantially orthogonal to the air flow direction F, as shown in FIG. It is a heat transfer tube called a multi-hole tube. The plurality of refrigerant flow paths P are formed in the air flow direction F in the flat heat transfer tubes 41, 42, 43,... In order to form the flat heat transfer tubes 41, 42, 43,. It is provided side by side. The pipe diameter of each refrigerant flow path P is very small, and one has a square shape of about 250 μm × about 250 μm, which is a so-called microchannel heat exchanger.

(2-3) Fin group As shown in FIGS. 2 to 4, the fin group 50 includes adjacent flat heat transfer tubes 41, 42, 43 at least between the adjacent flat heat transfer tubes 41, 42, 43,. ,... Are constituted by fins 50a and 50b arranged to be joined to at least one of. That is, the fin 50 group includes adjacent flat heat transfer tubes 41, such as a fin 50 a positioned between adjacent flat heat transfer tubes 41, 42 and a fin 50 b positioned between adjacent flat heat transfer tubes 42, 43. 42, 43,... Are separated from each other.

  Each of the fins 50a and 50b is a so-called corrugated fin formed by bending a plate-like member into a wave shape by about 90 degrees in a front view of the heat exchanger 10 in FIG. Specifically, as shown in FIG. 5, each fin 50a, 50b is formed by cutting a single plate-like member made of aluminum or an aluminum alloy along a solid line Re1 represented by a thick line, and then a solid line Re2 After being cut along the line, a mountain fold along the dotted line Dt1 and a valley fold along the one-dot broken line Dt2 are alternately performed to form a wave shape. Here, when the plate-like member is folded into a mountain and a valley, the plate-like member is bent by about 90 degrees.

  The fins 50a formed in this way are arranged so as to be sandwiched between the flat heat transfer tubes 41 and 42 as shown in FIGS. 3 and 4, and are formed on the flat surface 41b on the lower surface side of the flat heat transfer tubes 41. On the other hand, a folded portion 53 that is folded in a mountain is in contact with a folded portion 54 that is folded in a valley with respect to the flat surface 42 a that is the upper surface side of the flat heat transfer tube 42. Similarly, the fin 50b is disposed so as to be sandwiched between the flat heat transfer tubes 42 and 43, and the folded portion 53 that is folded in the flat surface 42b that is the lower surface side of the flat heat transfer tube 42 has a flat shape. The folded-back portions 54 that are valley-folded are in contact with the flat surface 43 a that is the upper surface side of the heat transfer tube 43. And each part 53 and 54 which flat heat-transfer tube 41,42,43, ... and each fin 50a, 50b are contacting as mentioned above is being fixed by brazing welding.

  As a result, the heat of the refrigerant flowing through the flat heat transfer tubes 41, 42, 43,... Is not only the surface of the flat heat transfer tubes 41, 42, 43,. Heat will be transferred to. Therefore, the heat transfer area of the heat exchanger 10 is increased, the heat exchange efficiency is improved, and the heat exchanger 10 itself can be made compact.

  The heat exchanger 10 according to the present embodiment is a so-called stacked heat exchanger in which flat heat transfer tubes 41, 42, 43,... And the fins 50a, 50b are alternately stacked in the vertical direction. is there. Therefore, the space | interval of each flat heat exchanger tube 41,42,43, ... can be ensured easily by the interposing fin 50a, 50b, and the assembly workability | operativity of the heat exchanger 10 can be improved.

  Here, as a plate | board thickness of fin 50a, 50b which concerns on this embodiment, about 0.1 mm is mentioned, for example.

(2-4) Detailed Configuration of Fins Each of the above-described fins 50a and 50b has two types of first fin portion 51 and second fin portion 52 having different shapes as already shown in FIGS. And folded portions 53 and 54 and a plurality of louvers 55.

(2-4-1) 1st fin part and 2nd fin part The 1st fin part 51 and the 2nd fin part 52 are the flat heat exchanger tubes 41, 42, 43 in the fins 50a, 50b folded back in a wave shape. Are plate-like portions that do not contact each other and are adjacent to each other. That is, as shown in FIGS. 3 and 4, the first fin portion 51 and the second fin portion 52 are arranged so that the plate thickness direction intersects the air flow direction F. Of the fins 50 a and 50 b, The part which spreads flatly from the peak part of the fin shape to the valley part. And the 1st fin part 51 and the 2nd fin part 52 are alternately arrange | positioned as shown to FIG.5,8,9, and as shown to FIG.6, 7, the width | variety along the air flow direction F is shown. It has a shape that is bilaterally symmetric with respect to the center line ln1 that is divided into two equal parts. Such 1st fin part 51 and 2nd fin part 52 have heat-transfer part 51a, 52a, upper water conveyance part 51b, 52b, and lower water conveyance part 51c, 52c, respectively.

  The heat transfer portions 51a and 52a are portions that mainly perform heat exchange with air, and the planes thereof are generally along the air flow direction F. With such a configuration of the heat transfer portions 51a and 52a, the ventilation resistance due to the provision of the fins 50a and 50b can be suppressed to a small value.

  The upper water guide portions 51b and 52b play a role of guiding the condensed water downward to the heat exchanger 10, and protrude upward from the heat transfer portions 51a and 52a. Specifically, the upper water guide portions 51b and 52b protrude upward along the vertical direction when the fins 50a and 50b are bent into corrugations, and the width thereof becomes narrower toward the tip portion. And has a triangular shape.

  The lower water guide portions 51c and 52c, like the upper water guide portions 51b and 52b, play a role of guiding the condensed water below the heat exchanger 10, and protrude downward from the heat transfer portions 51a and 52a. . Specifically, the lower water guide portions 51c and 52c protrude downward along the direction opposite to the upper water guide portions 51b and 52b, that is, in the vertical direction, when the fins 50a and 50b are bent into corrugations, respectively. It has an approximately triangular shape by narrowing the width toward the tip.

  In particular, in the present embodiment, the protruding amount d1a of the upper water guiding portion 51b of the first fin portion 51 is different from the protruding amount d2a of the upper water guiding portion 52b of the second fin portion 52, but the second fin portion 52 is. Is equal to the protruding amount d2b of the lower water guide portion 52c. The protruding amount d1b of the lower water guiding portion 51c of the first fin portion 51 is different from the protruding amount d2b of the lower water guiding portion 52c of the second fin portion 52, but the protruding amount of the upper water guiding portion 52b of the second fin portion 52. It is equal to d2a. For example, the amount of the upper water guide portion 51b of the first fin portion 51 protruding from the flat upper end portion of the heat transfer portion 51a (that is, the protrusion amount d1a), and the lower water guide portion 52c of the second fin portion 52 is the heat transfer portion 52a. The amount of protrusion from the flat lower end portion (ie, the protrusion amount d2b) can be about 2 mm. The amount by which the lower water guide portion 51c of the first fin portion 51 protrudes from the flat lower end portion of the heat transfer portion 51a (that is, the protrusion amount d1b), and the upper water guide portion 52b of the second fin portion 52 is the flatness of the heat transfer portion 52a. The amount protruding from the upper end portion (that is, the protruding amount d2a) can be about 0.5 mm. In particular, the protrusion amounts d1a, d2b of the upper water guide portion 51b of the first fin portion 51 and the lower water guide portion 52c of the second fin portion 52 are the widths of the flat heat transfer tubes 41, 42, 43,. The protrusions d1b, d2a of the lower water guide portion 51c of the first fin portion 51 and the upper water guide portion 52b of the second fin portion 52 are higher than the thickness Pd2, and the flat heat transfer tubes 41, 42, 43,. It is lower than the thickness Pd2 (see FIGS. 3, 4 and 9).

  Here, in the present embodiment, the projection amounts d1a and d1b of the water guide portions 51b and 51c in the first fin portion 51 are the average values of the projection amounts d1a and d1b of the water guide portions 51b and 51c. Is determined to be longer than the thickness Pd2 of 42, 43,. Similarly, the projections d2a and d2b of the water guide portions 52b and 52c in the second fin portion 52 are flat heat transfer tubes 41, 42, 43, and an average value of the projection amounts d2a and d2b of the water guide portions 52b and 52c. Is determined to be longer than the thickness Pd2. This is in order to maintain the so-called drainage performance in which the condensed water flows reliably below the fins 50a and 50b.

  Moreover, as an angle of the front-end | tip part of the lower water guide part 51c and the upper water guide part 52b with a small protrusion amount, about 10 to 40 degree | times is mentioned, for example. On the other hand, as an angle of the tip part of upper water guide part 51b and lower water guide part 52c with big projection amount, about 30 degrees-60 degrees are mentioned, for example.

  In the 1st fin part 51 and the 2nd fin part 52 which have the above structure, when the 2nd fin part 52 is located in the side of the 1st fin part 51 (refer FIG. 8), the 1st fin part 51 of FIG. The upper water guide portion 51 b protrudes above the upper water guide portion 52 b of the second fin portion 52. On the contrary, the lower water guide portion 52 c of the second fin portion 52 protrudes below the lower water guide portion 51 c of the first fin portion 51. When the flat heat transfer tubes 41, 42, 43 are inserted into the fins 50a, 50b, the lower water guide portion 51c of the first fin portion 51 and the upper water guide portion 52b of the second fin portion 52 are, as shown in FIGS. Although the thickness Pd2 of the flat heat transfer tubes 41, 42, 43,... Does not exceed, the upper water guide portion 51b of the first fin portion 51 and the lower water guide portion 52c of the second fin portion 52 are flat heat transfer tubes 41, The thickness Pd2 of 42, 43,...

  Further, as already described, the first fin portion 51 and the second fin portion 52 have a symmetrical shape with respect to the center line ln1, and therefore, the first fin portion 51 and the second fin portion 52 according to the present embodiment It can be said that the two fin portions 52 are point-symmetric with each other, that is, the first fin portion 51 has a shape in which the second fin portion 52 is turned upside down. Therefore, the front edge length of the first fin portion 51 according to the present embodiment is the same length as the front edge length of the second fin portion 52.

  Here, the reason why the first fin portion 51 and the second fin portion 52 are shaped as shown in FIGS. 6 and 7 will be briefly described. 10 and 11 show an example of a conventional first fin portion 151 and second fin portion 152.

  First, as shown in FIGS. 10 and 11, in the first fin portion 151, the protruding amount of the upper water guiding portion 151 b and the protruding amount of the lower water guiding portion 151 c are the same, and the upper water guiding portion 152 b is also in the second fin portion 152. And the amount of protrusion of the lower water guide portion 152c are the same. In this case, it can be said that the first fin portion 151 and the second fin portion 152 are not symmetrical with each other and are fin portions having completely different shapes. Furthermore, each of the first fin portion 151 and the second fin portion 152 has a shape that is vertically symmetric and laterally symmetric.

  Here, the fins having the first fin portion 151 and the second fin portion 152 are formed by bending a single plate-like member, like the fins 50a and 50b according to the present embodiment. Then, the projecting amount of each of the water guiding portions 151b and 151c of the first fin portion 151 is set to be larger than the fin pitch between the first fin portion 151 and the second fin portion 152 when the fin is bent into a wave shape. Thus, when the water guide portions 151b and 151c are formed, the protruding amount of the water guide portions 152b and 152c of the second fin portion 152 is smaller than the water guide portions 151b and 152c of the first fin portion 151. That is, the length of the front edge of the second fin portion 152 is much shorter than the length of the front edge of the first fin portion 151.

  In this case, the first fin portion 151 and the second fin portion 152 when the fin is bent into a corrugated shape are adjacent to each other in the thickness direction, but the surface area of the first fin portion 151 is the second fin portion. Therefore, the amount of the brazing material of the first fin portion 151 is larger than the amount of the brazing material of the second fin portion 152. Thus, when a difference occurs in the amount of brazing material, the amount of brazing material required to join the fin and the flat heat transfer tube is the same on the first fin portion 151 side and the second fin portion 152 side. However, there is a phenomenon that there is too much brazing material on the first fin portion 151 side, and conversely, there is too little brazing material on the second fin portion 152 side. Then, on the first fin portion 151 side where the amount of the brazing material is too large, even the brazing material that should not be melted, such as the portion that requires strength, melts, and erosion (wax erosion) occurs. End up. The melted brazing material may enter, for example, the opening 155a on the fin, or may act in the direction in which the louver 155 formed by cutting and raising is laid to block the opening 155a with the louver 155.

  However, as shown in FIGS. 6 and 7, the first fin portion 51 and the second fin portion 52 according to the present embodiment are not symmetrical in the vertical direction although they are bilaterally symmetric, and the first fin portion 51 and the second fin portion. The parts 52 have shapes that are point-symmetric with respect to each other. Therefore, the surface area of the first fin portion 51 and the surface area of the second fin portion 52 are equal. Therefore, the amount of brazing material is uniform between the first fin portion 51 and the second fin portion 52, and erosion or the like can be prevented.

  Further, when the flat heat transfer tubes 41, 42, 43,... Are inserted into the fins 50a, 50b, the flat tubes 42 located between the fins 50a, 50b as shown in FIGS. The fins 50a and the fins 50b are arranged alternately. Therefore, the condensed water is transferred to the heat transfer surface 52a from the upper water guide portion 52b of the second fin portion 52 in the fin 50b through the lower water guide portion 51c of the first fin portion 51 and the flat heat transfer tube 42 in the fin 50a. It will be transmitted to the lower water guide portion 51 c of the first fin portion 51 and the flat heat transfer tube 43 in the fin 50 b. Therefore, not only can the brazing material be made uniform, but also the drainage can be maintained.

  In addition, in FIG. 10, 11, in order to make it easy to compare with the 1st fin part 51 and the 2nd fin part 52 which concern on this embodiment, the protrusion amount of each water conveyance part 151b, 151c of the 1st fin part 151 is as follows. The amount of protrusion of the upper water guide 51b and the lower water guide 52c according to the present embodiment shown in FIGS. Furthermore, the protruding amount of each of the water guiding portions 152b and 152c of the second fin portion 152 is the same as the protruding amount of the lower water guiding portion 51c and the upper water guiding portion 52b according to the present embodiment shown in FIGS.

(2-4-2) Folded portions Folded portions 53 and 54 are portions that connect the first fin portion 51 and the second fin portion 52 that are adjacent to each other when the fins 50a and 50b are folded into corrugations. . The widths d3a and d4a of the folded portions 53 and 54 in the direction X (see FIGS. 5 and 8) intersecting the air flow direction F correspond to the distance between the first fin portion 51 and the second fin portion 52, respectively. On the other hand, the widths d3b, d4b of the folded portions 53, 54 along the air flow direction F are along the air flow direction F of the flat heat transfer tubes 41, 42, 43,. Substantially coincides with the width Pd1.

  Here, the width d3a of the folded portion 53 is equal to the width d4a of the folded portion 54, and can be about 1.5 mm, for example. The width d3b of the folded portion 53 is equal to the width d4b of the folded portion 54, and may be about 18 mm, for example.

(2-4-3) Louver As shown in FIGS. 3 and 12, the plurality of louvers 55 protrude in the plate thickness direction from the heat transfer portions 51 a and 52 a of the first fin portion 51 and the second fin portion 52. Are arranged along the air flow direction F. As shown in FIG. 4, the louver 55 has an elongated rectangular shape along the arrangement direction of adjacent flat heat transfer tubes 41, 42, 43,..., That is, in the vertical direction. As shown in FIG.

  Such a louver 55 is formed by cutting and raising from a part of each of the heat transfer portions 51 a and 52 a of the first fin portion 51 and the second fin portion 52. Specifically, each louver 55 is formed by being cut and raised so as to incline so as to incline upstream in the air flow direction F as shown in FIG. Furthermore, the opening 55a is formed in each heat-transfer part 51a, 52a because each louver 55 is cut and raised (refer FIG. 6, 7).

  In the present embodiment, the inclination angle θ1 at which each louver 55 is inclined with respect to each heat transfer section 51a, 52a and the protrusion height h1 of the louver 55 from each heat transfer section 51a, 52a are constant. Is taken as an example. However, the inclination angle θ1 and the protrusion height h1 may be different for each louver 55.

(3) Flow of Refrigerant A mode in which the refrigerant flows into the heat exchanger 10 having the above configuration and the refrigerant flows out of the heat exchanger 10 will be briefly described. Here, a case where the air conditioner performs a heating operation, that is, a case where the heat exchanger 10 functions as an evaporator will be described.

  First, a liquid refrigerant or a gas-liquid two-phase refrigerant flows into the diversion header 20. This refrigerant is divided approximately equally into the refrigerant flow paths P of the flat heat transfer tubes 41, 42, 43,... In the flat heat transfer tube group 40.

  While the refrigerant flows through the refrigerant flow paths P of the flat heat transfer tubes 41, 42, 43,..., The fin group 50 and the flat heat transfer tube group 40 themselves are warmed by the air supplied by the blower (not shown). The refrigerant flowing inside the refrigerant flow path P is also warmed. By applying heat to the refrigerant in this way, the refrigerant gradually evaporates into a gas phase state in the process of passing through the refrigerant flow path P. In this process, moisture in the air cooled by the heat of the refrigerant adheres to the surface of the heat exchanger 10 as condensed water. The condensed water eventually flows downward of the heat exchanger 10 via the upper water guide portions 51b and 52b and the lower water guide portions 51c and 52c of the first fin portion 51 and the second fin portion 52, respectively.

  Thereafter, the refrigerant in a gas phase state passes through each refrigerant flow path P such as the flat heat transfer tubes 42 and 43, and then merges by the merge header 30 to become one refrigerant flow and flows out from the heat exchanger 10. I will do it.

(4) Features (4-1)
According to this heat exchanger 10, in the first fin portion 51 and the second fin portion 52 adjacent to each other, the protrusion amounts d1a and d2a of the upper water guide portions 51b and 52b are different from each other, and the protrusion amounts of the lower water guide portions 51c and 52c. d1b and d2b are also different from each other. The protrusion amount d1a of the upper water guide portion 51b of the first fin portion 51 is equal to the protrusion amount d2b of the lower water guide portion 52c of the second fin portion 52, and the protrusion amount d1b of the lower water guide portion 51c of the first fin portion 51 is The protrusion amount d2a of the upper water guide portion 52b of the second fin portion 52 is equal. Accordingly, the sum of the areas of the upper water guiding portion 51b and the lower water guiding portion 51c in the first fin portion 51 is equal to the sum of the areas of the upper water guiding portion 52b and the lower water guiding portion 52c in the second fin portion 52. Therefore, the fins 50a, 50b and the flat heat transfer tubes 41, 42, 43,... Are not sufficiently in contact with each other due to the difference in the amount of brazing material, or so-called erosion that unnecessarily melts the brazing material occurs. Can be prevented. Accordingly, the fins 50a, 50b and the flat heat transfer tubes 41, 42, 43,.

(4-2)
Moreover, in this heat exchanger 10, the 1st fin part 51 and the 2nd fin part 52 have a left-right symmetrical shape with respect to the centerline ln1 which bisects the width along the air flow direction F. . That is, it can be said that the first fin portion 51 and the second fin portion 52 have a point-symmetric relationship with each other. Thereby, the sum total of the area of the upper water guide part 51b and the lower water guide part 51c in the 1st fin part 51 and the sum total of the area of the upper water guide part 52b and the lower water guide part 52c in the 2nd fin part 52 correspond substantially. Therefore, it is possible to further prevent a difference in the amount of brazing material between the first fin portion 51 and the second fin portion 52.

(4-3)
Moreover, in this heat exchanger 10, upper water conveyance part 51b, 52b and lower water conveyance part 51c, 52c have a triangular shape which becomes narrow toward the front-end | tip part. As a result, the fins 50a and 50b are secured with portions that come into contact with the flat heat transfer tubes 41, 42, 43,.

  In particular, in this embodiment, the upper water guide portions 51b and 52b and the lower water guide portions 51c and 52c have a triangular shape as shown in FIGS. For this reason, the length of each water conveyance part 51b, 52b, 51c, 52c is fully securable. Therefore, the condensed water can be reliably guided below the fins 50a and 50b without accumulating in the vicinity of the fins 50a and 50b.

(4-4)
Further, in this heat exchanger 10, as shown in FIG. 9, the fins 50a and 50b are wave-shaped with a plate-like member of about 90 degrees between adjacent flat heat transfer tubes 41, 42, 43,. It is formed by being bent. That is, the fins 50a and 50b according to the present embodiment are so-called corrugated fins. Even in this case, the so-called erosion that the fins 50a, 50b and the flat heat transfer tubes 41, 42, 43,... Do not sufficiently contact or unnecessarily melt the brazing material due to the difference in the amount of brazing material. Can be prevented. Therefore, the fins 50a, 50b and the flat heat transfer tubes 41, 42, 43,.

(5) Modification (5-1) Modification A
In the above-described embodiment, the case where the upper water guide portions 51b and 52b and the lower water guide portions 51c and 52c have an approximately triangular shape as illustrated in FIGS. However, the shapes of the upper water guide portions 51b and 52b and the lower water guide portions 51c and 52c are not limited to this. Examples of other shapes of the upper water guide portions 51b and 52b and the lower water guide portions 51c and 52c include a case where the upper water guide portions 51b and 52b are so-called tapered shapes, although not triangular.

(5-2) Modification B
In the above embodiment, the case where the bending angle of the fins 50a and 50b is about 90 degrees has been described. However, the bending angle of the fins 50a and 50b may not be about 90 degrees. For example, the first fin portion 51 and the second fin portion 52 are inclined at a predetermined angle with respect to the vertical direction and are different from each other. It may extend toward.

(5-3) Modification C
In the above embodiment, the case where the fins 50a and 50b are corrugated fins formed by bending a single plate-like member has been described. However, the types of fins 50a and 50b are not limited to corrugated fins. For example, the present invention can be applied even to a fin that does not have the folded-back portions 53 and 54 and in which the first fin portion and the second fin portion are formed of separate plate-like members.

DESCRIPTION OF SYMBOLS 10 Heat exchanger 20 Split header 30 Merge header 40 Flat heat-transfer tube group 41, 42, 43 Flat heat-transfer tube 41a, 41b, 42a, 42b, 43a, 43b Flat surface 50 Fin group 50a, 50b Fin 51 1st fin part 52 1st 2 fin part 51a, 52a Heat-transfer part 51b, 52b Upper water conveyance part 51c, 52c Lower water conveyance part 55 Louver 55a Opening

JP 2008-101847 A

Claims (4)

Fins (50a, 50b) having plate-like first fin portions (51) and second fin portions (52) which are arranged so that the plate thickness direction intersects the air flow direction (F) and are adjacent to each other. When,
A plurality of heat transfer tubes (41, 42, 43,...) Inserted into the fins (50a, 50b) so as to intersect the air flow direction;
With
The first fin portion (51) and the second fin portion (52) include a heat transfer portion (51a, 52a) that performs heat exchange with air, and an upper water guide portion (51b) protruding upward from the heat transfer portion. , 52b) and a lower water guiding portion (51c, 52c) protruding downward from the heat transfer portion,
The amount of protrusion of the upper water guide portion (51b) of the first fin portion (51) is different from the amount of protrusion of the upper water guide portion (52b) of the second fin portion (52), and the second fin. Equal to the amount of protrusion of the lower water guide portion (52c) of the portion (52),
The amount of protrusion of the lower water guide portion (51c) of the first fin portion (51) is different from the amount of protrusion of the lower water guide portion (52c) of the second fin portion (52), and the second fin. It is equal to the protruding amount of the upper water guide part (52b) of the part (52),
Heat exchanger (10). The first fin part (51) and the second fin part (52) have a symmetrical shape with respect to a center line (ln1) that bisects the width along the air flow direction (F). ing,
The heat exchanger (10) according to claim 1. The upper water guide part (51b, 52b) and the lower water guide part (51c, 52c) have a shape whose width becomes narrower toward the tip part,
The heat exchanger (10) according to claim 1 or 2. The fins (50a, 50b) are formed by bending a plate-like member into a wave shape by about 90 degrees between the adjacent heat transfer tubes (41, 42, 43, ...).
The heat exchanger (10) according to any one of claims 1 to 3.

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