JP6545357B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger for discharging water droplets adhering to the surface of a fin.

  2. Description of the Related Art Conventionally, a corrugated fin type heat exchanger used for an air conditioner such as a packaged air conditioner and a multi-air conditioner for buildings is known as a heat exchanger. The corrugated fin type heat exchanger includes a plurality of flat tubes arranged at intervals, and a corrugated fin provided between two flat tubes, and the refrigerant flowing inside the flat tube And heat exchange with the air passing through the gaps of the corrugated fins. When the corrugated fin type heat exchanger acts as an evaporator, water droplets may adhere to the surface of the fins. Further, in the corrugated fin type heat exchanger, when the defrosting operation is performed, the frost adhering to the surface of the fin may be melted and the water may be deposited, whereby water droplets may adhere to the surface of the fin. As described above, when the water droplets adhere to the surface of the fins and stay there, they become air flow resistance when air flows, so the heat transfer performance of the heat exchanger is lowered. For this reason, a heat exchanger has been proposed in which the fins are inclined with respect to the horizontal direction. Thus, the water droplets adhering to the fins flow on the fins and are drained downward through the fluid path provided at the junction of the flat tube and the fins.

  Patent Document 1 discloses a heat exchanger in which the fins are inclined from the horizontal direction, and a plurality of cut and raised portions are provided on the surfaces of the fins. The cut-and-raised part is a piece in which two cuts parallel to the surface of the fin are made, and starting from the cut, a trapezoidal shape is raised from the surface of the fin. In the cutting and raising, the portion rising from the surface of the fin is the rising side. The rising side is inclined in parallel with the inclination direction of the fin. As a result, the water droplets attached to the cut and raised portions flow toward the junction between the flat tube and the fin, similarly to the water droplets attached to the fins. Further, Patent Document 1 discloses a technique in which a plurality of openings are provided in a joint between a flat tube and a fin, and water introduced to the joint is drained through the opening. As a result, surface tension is generated in the water at the bonding portion, and the water is held at the bonding portion, thereby preventing smooth drainage.

Unexamined-Japanese-Patent No. 2013-250016

  However, in the heat exchanger disclosed in Patent Document 1, since the plurality of openings are formed in the joint, the joint area is reduced and the heat transfer performance of the heat exchanger is reduced.

  The present invention has been made to solve the problems as described above, and provides a heat exchanger that improves drainage while maintaining heat transfer performance.

In the heat exchanger according to the present invention, a plurality of flat tubes arranged at intervals with their flat surfaces parallel to each other, and between one flat tube adjacent to the plurality of flat tubes and the other flat tube The corrugated fin is a corrugated joint having a first junction joined to the flat surface of one flat tube at one convex portion of the corrugated shape, and a flat at the other convex portion of the corrugated shape. A second joint joined to the flat surface of the pipe, and a fin for heat exchange with air between the first joint and the second joint, the fin being a first joint A fin surface connecting the first portion and the second joint, a slit longitudinally opened in a direction along the flat surface between the first joint and the second joint; There is a different slope to the fin surface continuously from the vicinity of the joint or second joint to the slit Has an inclined portion that, and the direction in which the plurality of the flat tubes extending when the vertical, inclined portion, the first joint portion or the second bonding portion side becomes inclined downward toward the slit A plurality of inclined portions are provided in the long side direction of the flat tube, and the length of the long side direction of the flat tube becomes shorter from the upstream side to the downstream side in the direction in which air flows .

  According to the present invention, water droplets adhering to the surface of the fin are guided to the slit, hit the inclined portion, guided downward, and dropped downward from the slit. Thus, when draining, an opening part is unnecessary to the 1st junction part and 2nd junction part to which a flat pipe and a fin are joined. For this reason, drainage can be improved while maintaining the heat transfer performance.

BRIEF DESCRIPTION OF THE DRAWINGS It is a circuit diagram which shows the air conditioner 1 which concerns on Embodiment 1 of this invention. It is a perspective view which shows the heat exchanger 5 which concerns on Embodiment 1 of this invention. It is front sectional drawing which shows the heat exchanger 5 which concerns on Embodiment 1 of this invention. It is a perspective view which shows the heat exchanger 105 which concerns on Embodiment 2 of this invention. It is a perspective view which shows the heat exchanger 205 which concerns on Embodiment 3 of this invention. It is a perspective view which shows the heat exchanger 305 which concerns on Embodiment 4 of this invention. It is a perspective view which shows the heat exchanger 405 which concerns on Embodiment 5 of this invention. It is a perspective view which shows the heat exchanger 505 which concerns on Embodiment 6 of this invention. It is a perspective view which shows the heat exchanger 605 which concerns on Embodiment 7 of this invention.

Embodiment 1
Hereinafter, an embodiment of a heat exchanger according to the present invention will be described with reference to the drawings. FIG. 1 is a circuit diagram showing an air conditioner 1 according to Embodiment 1 of the present invention. The air conditioner 1 will be described based on FIG. As shown in FIG. 1, the air conditioner 1 includes a refrigerant circuit 2, an outdoor blower 8, and an indoor blower 9. In the refrigerant circuit 2, the compressor 3, the flow path switching unit 4, the heat exchanger 5, the expansion unit 6, and the indoor heat exchanger 7 are connected by piping, and the refrigerant flows.

  The compressor 3 compresses a refrigerant. The flow path switching unit 4 switches the flow direction of the refrigerant in the refrigerant circuit 2. The flow path switching unit 4 switches whether the refrigerant discharged from the compressor 3 flows to the heat exchanger 5 or to the indoor heat exchanger 7, whereby the cooling operation, the heating operation, or the defrosting operation is performed. Both are done. The heat exchanger 5 is provided, for example, outdoors, and exchanges heat between the outdoor air and the refrigerant. The outdoor blower 8 is provided, for example, outside the room, and blows the outdoor air to the heat exchanger 5.

  The expansion unit 6 is for expanding and depressurizing the refrigerant, and is, for example, an electromagnetic expansion valve whose opening degree is adjusted. The indoor heat exchanger 7 is provided, for example, indoors, and exchanges heat between indoor air and the refrigerant. The indoor blower 9 is provided, for example, indoors, and sends indoor air to the indoor heat exchanger 7.

  FIG. 2 is a perspective view showing the heat exchanger 5 according to Embodiment 1 of the present invention. Next, the heat exchanger 5 will be described in detail. As shown in FIG. 2, the heat exchanger 5 includes a plurality of flat tubes 20 and corrugated fins 30.

  The flat tube 20 extends in the gravity direction (arrow Z direction), and the cross section perpendicular to the gravity direction, which is the longitudinal direction (arrow Z direction), has an elliptical shape. A plurality of refrigerant channels 21 in which the refrigerant flows are formed in the flat pipe 20 in the long side direction (the arrow Y direction) of the flat pipe 20, and the refrigerant flows in the refrigerant channels 21 in the vertical direction. The plurality of flat tubes 20 are arranged at intervals in the short side direction (arrow X direction) of the flat tube 20. That is, the plurality of flat tubes 20 are arranged at intervals such that the flat surfaces 20a thereof become parallel.

  The corrugated fin 30 is provided between two adjacent flat tubes 20 and has a wave shape when viewed from the short side direction (the arrow X direction), and the first joint 31 and the second joint 32 are formed. And a fin portion 33. The first bonding portion 31 is one in which a convex portion in a corrugated shape is bonded to the flat surface 20 a of one flat tube 20. The second joint portion 32 is one in which the other convex portion of the corrugated shape is joined to the flat surface 20 a of the other flat tube 20. The fin 33 exchanges heat with air between the first joint 31 and the second joint 32. The corrugated fins 30 are corrugated by being folded in opposite directions at the first junction 31 and the second junction 32.

  Here, the first bonding portion 31 and the second bonding portion 32 are formed in parallel to the long side direction (the arrow Y direction). That is, the fin portion 33 is formed in parallel with the long side direction (the arrow Y direction). Then, air flows between the fin portions 33 in the corrugated fins 30 (open arrows). The flat tube 20 through which the refrigerant flows is joined to the corrugated fins 30 in contact with the air at the fin portion 33, whereby the refrigerant and the air exchange heat. Moreover, although it is desirable that the surface of the corrugated fin 30 has hydrophilicity, the surface of the corrugated fin 30 may have water repellency.

  The fin portion 33 is inclined downward to the short side direction (the arrow X direction) from the first joint portion 31 to the second joint portion 32. Thus, the water droplets attached to the fin portion 33 flow from the first bonding portion 31 side to the second bonding portion side. Further, the fin portion 33 is formed with a slit 40 which is cut out so as to extend in the long side direction (arrow Y direction). The slits 40 are formed at both ends in the short side direction (arrow X direction) of the fin portion 33, and the slits 40 on the first bonding portion 31 side are referred to as upstream slits 40a, respectively, and the second bonding portion The slit 40 on the 32 side is referred to as the downstream side slit 40 b. Thus, the slit 40 is opened longitudinally in the direction along the flat surface 20 a between the first bonding portion 31 and the second bonding portion 32. The number of slits 40 may be one or three or more. When the number of the slits 40 is one, the slits 40 are preferably provided at the end of the fin 33 on the second bonding portion 32 side. Further, the end of the slit 40 on the flat tube 20 side is at a position of 2 mm or less from the flat tube 20.

  Further, the fin portion 33 is formed with a sub slit 50 which is cut out so as to extend in a direction different from the slit 40. In the first embodiment, the sub slit 50 is cut out so as to extend in the short side direction (the arrow X direction). And six sub slits 50 are formed in the long side direction (arrow Y direction) between the upstream slit 40 a and the downstream slit 40 b. The number of sub slits 50 may be five or less, or seven or more.

  FIG. 3 is a front cross-sectional view showing the heat exchanger 5 according to Embodiment 1 of the present invention. As shown in FIG. 3, the fin portion 33 has a fin surface portion 33 a, an inclined portion 41 and a sub-inclined portion 51. The fin surface portion 33 a connects the first bonding portion 31 and the second bonding portion 32. The inclined portion 41 has a different inclination with respect to the fin surface portion 33 a continuously from the vicinity of the first joint portion 31 or the second joint portion 32 to the slit 40. The inclined portion 41 is, for example, a portion in which the fin portion 33 is bent, and closes a portion of the slit 40. The inclined portions 41 are formed at both ends in the short side direction (arrow X direction) of the fin portion 33, and the inclined portions 41 on the first joint 31 side are respectively referred to as the upstream side inclined portions 41a. The inclined portion 41 on the side of the joint portion 32 is referred to as the downstream side inclined portion 41 b. The number of inclined portions 41 may be one or three or more. When the number of the inclined portions 41 is one, it is preferable that the inclined portion 41 be provided at the end of the fin portion 33 on the second bonding portion 32 side. Moreover, the height of the both ends of a long side direction (arrow Y direction) of the inclination part 41 is equal. In addition, it is desirable that one end of the inclined portion 41 be close to the flat tube 20 by 2 mm or less. That is, the sloped portion 41 has different slopes with respect to the fin surface portion 33a continuously from the first bonding portion 31 or the second bonding portion 32 to the slit 40 from the portion of 2 mm or less.

  In the first embodiment, the inclined portion 41 is a portion in which a portion of the fin portion 33 is cut out and the remaining portion is bent, and the slit 40 is formed by bending a portion of the fin portion 33. It is an opening formed. In the first embodiment, the sloped portion 41 protrudes upward and downward of the fin portion 33, but may protrude downward only. In addition, when the direction (arrow Y direction) in which the plurality of flat tubes 20 extend is vertical, the inclined portion 41 is inclined downward toward the slit 40 from the first joint portion 31 side or the second joint portion 32 side. It has become. That is, in the upstream side inclined portion 41 a, the first bonding portion 31 side protrudes above the fin portion 33, and the second bonding portion 32 side protrudes below the fin portion 33. Further, on the downstream side inclined portion 41 b, the first bonding portion 31 side protrudes below the fin portion 33, and the second bonding portion 32 side protrudes above the fin portion 33.

  The sub-inclined portion 51 is a part of the fin portion 33 and is inclined with respect to the other portion of the fin portion 33. The sub-inclined portion 51 is provided to extend in the short side direction (arrow X direction), thereby improving the heat transfer performance of the corrugated fin 30. For example, a portion of the fin portion 33 is bent, and the sub-inclined portion 51 closes a portion of the sub-slit 50. Six auxiliary inclined portions 51 are formed in the long side direction (the arrow Y direction) between the upstream side inclined portion 41 a and the downstream side inclined portion 41 b. In addition, the number of the auxiliary | assistant inclination parts 51 may be five or less, and seven or more may be sufficient.

  In the first embodiment, the heat exchanger 5 is used as the outdoor heat exchanger 5, but may be applied to the indoor heat exchanger 7.

  Next, the operation mode of the air conditioner 1 will be described. The air conditioner 1 has a cooling operation, a heating operation, and a defrosting operation as operation modes. In the cooling operation, the refrigerant flows in the order of the compressor 3, the flow path switching unit 4, the heat exchanger 5, the expansion unit 6, and the indoor heat exchanger 7 (broken line arrow in FIG. 1). It exchanges heat with the refrigerant and is cooled. In the heating operation, the refrigerant flows in the order of the compressor 3, the flow path switching unit 4, the indoor heat exchanger 7, the expansion unit 6, and the heat exchanger 5 (solid arrows in FIG. 1). The heat is exchanged with the refrigerant and heated. In the defrosting operation, the refrigerant flows in the order of the compressor 3, the flow path switching unit 4, the heat exchanger 5, the expansion unit 6, and the indoor heat exchanger 7 (broken line arrow in FIG. 1) To remove

  Next, the operation of each operation mode of the air conditioner 1 will be described. First, the cooling operation will be described. In the cooling operation, the refrigerant drawn into the compressor 3 is compressed by the compressor 3 and discharged in a high-temperature, high-pressure gas state. The refrigerant in the high-temperature high-pressure gas state discharged from the compressor 3 passes through the flow path switching unit 4 and flows into the heat exchanger 5, and in the heat exchanger 5, the outdoor air blown by the outdoor blower 8 Heat is exchanged to condense and liquefy. The condensed refrigerant in the liquid state flows into the expansion portion 6, and is expanded and reduced in pressure in the expansion portion 6 to be in a gas-liquid two-phase state. Then, the refrigerant in the gas-liquid two-phase state flows into the indoor heat exchanger 7, and in the indoor heat exchanger 7, it exchanges heat with indoor air blown by the indoor blower 9 to be vaporized and gasified. At this time, the room air is cooled and cooling is performed. The evaporated refrigerant in the gas state passes through the flow path switching unit 4 and is drawn into the compressor 3.

  Next, the heating operation will be described. In the heating operation, the refrigerant drawn into the compressor 3 is compressed by the compressor 3 and discharged in a high-temperature and high-pressure gas state. The refrigerant in the high temperature / high pressure gas state discharged from the compressor 3 passes through the flow path switching unit 4 and flows into the indoor heat exchanger 7, and in the indoor heat exchanger 7, the room is blown by the indoor blower 9. Heat exchange with air to condense and liquefy. At this time, room air is warmed and heating is performed. The condensed refrigerant in the liquid state flows into the expansion portion 6, and is expanded and reduced in pressure in the expansion portion 6 to be in a gas-liquid two-phase state. Then, the refrigerant in the gas-liquid two-phase state flows into the heat exchanger 5, and in the heat exchanger 5, the refrigerant exchanges heat with the outdoor air blown by the outdoor blower 8 to be vaporized and gasified. The evaporated refrigerant in the gas state passes through the flow path switching unit 4 and is drawn into the compressor 3.

  Next, the defrosting operation will be described. In the air conditioner 1, frost may adhere to the heat exchanger 5 when the heating operation is performed. A defrost operation is performed to remove the frost. In the defrosting operation, the refrigerant drawn into the compressor 3 is compressed by the compressor 3 and discharged in a high-temperature, high-pressure gas state. The high-temperature high-pressure gas refrigerant discharged from the compressor 3 passes through the flow path switching unit 4 and flows into the heat exchanger 5 to melt the frost adhering to the heat exchanger 5. Then, the refrigerant exchanges heat with the outdoor air in the heat exchanger 5 to condense and liquefy. The condensed refrigerant in the liquid state flows into the expansion unit 6. At this time, the expansion portion 6 is fully opened, and the refrigerant flows into the indoor heat exchanger 7 in a liquid state. Then, the refrigerant in the liquid state flows into the indoor heat exchanger 7, and in the indoor heat exchanger 7, it exchanges heat with indoor air to be vaporized and gasified. The evaporated refrigerant in the gas state passes through the flow path switching unit 4 and is drawn into the compressor 3.

  Next, the flow of water attached to the heat exchanger 5 according to the first embodiment will be described. When the heat exchanger 5 acts as an evaporator, when the air flows to the heat exchanger 5, the surfaces of the flat tubes 20 and the corrugated fins 30 become lower than the temperature of the air. For this reason, water vapor in the air condenses on the surfaces of the flat tube 20 and the corrugated fins 30. Moreover, when the surface of the flat tube 20 and the corrugated fin 30 becomes 0 degrees C or less, frost formation will arise on the surface of the flat tube 20 and the corrugated fin 30. FIG. In particular, in the fin portion 33 of the corrugated fin 30, the inclined portion 41 at a position close to the flat tube 20 has a high heat transfer coefficient, and therefore, the amount of frost formation is large. When the frost adheres to the surface of the corrugated fins 30 and the air passage through which the air passes is blocked and the performance of the heat exchanger 5 is reduced and the heating operation capability is reduced, the defrosting operation is performed. In the defrosting operation, when the high temperature refrigerant flows to the heat exchanger 5, the frost adhering to the outer surface of the flat tube 20 and the corrugated fins 30 melts, and drain water is deposited. As a result, the defrosting operation is completed and the heating operation is resumed. In this manner, water droplets adhere to the fin portion 33 of the corrugated fin 30.

  The water droplets adhering to the fin portion 33 travel from the first joint portion 31 side along the fin portion 33 which is inclined to the short side direction (the arrow X direction) from the first joint portion 31 to the second joint portion 32. It flows to the second joint 32 side. The water droplets adhering to the vicinity of the first bonding portion 31 fall from the upstream slit 40 a to the fin portion 33 below. Further, the water droplets attached to the upstream inclined portion 41 a flow along the upstream inclined portion 41 a and fall from the upstream slit 40 a to the lower fin portion 33. Furthermore, the water droplets attached to the central portion between the first bonding portion 31 and the second bonding portion 32 are trapped by the downstream side inclined portion 41b, and flow along the downstream side inclined portion 41b, from the downstream side slit 40b downward. Fall on the fin section 33 of the

  Therefore, since the water droplet does not reach the second bonding portion 32, the surface tension prevents the water droplet from being held between the corrugated fins 30 and the flat tube 20. Therefore, the fall of the heat transfer performance by the ventilation resistance increasing by residual water can be suppressed. Moreover, holding | maintenance between the corrugated fin 30 and the flat pipe 20 is similarly suppressed also in the drain water fuse | melted at the time of a defrost. For this reason, during the defrosting operation, it is possible to suppress a decrease in heat transfer performance due to an increase in defrosting time and an increase in ventilation resistance caused by solidification of residual water.

  At that time, since the downstream side inclined portion 41b is inclined toward the center in the short side direction (arrow X direction) in the fin portion 33, the water droplets are inclined along the downstream side inclined portion 41b. It flows from the second joint 32 side, which is the opposite direction to the direction, to the first joint 31 side, and falls from the downstream side slit 40 b to the lower fin portion 33. Therefore, the water droplets do not fall to the second bonding portion 32 side, but fall to the central portion of the lower fin portion 33. Moreover, since the downstream side inclined part 41b protrudes above the fin part 33, a water droplet is easy to be trapped by the downstream side inclined part 41b. Further, the water droplets attached to the downstream side inclined portion 41 b flow along the downstream side inclined portion 41 b and fall from the downstream side slit 40 b to the fin portion 33 below. Here, the end on the flat tube 20 side of the downstream side slit 40b is at a position of 2 mm or less from the flat tube 20, and is provided at the end of the fin portion 33. The amount of water droplets adhering to the side of the joint 32 is small. That is, most of the water adhering to the fin portion 33 falls from the upstream slit 40 a or the downstream slit 40 b to the lower fin portion 33.

  When the number of the slits 40 and the inclined portions 41 is one, if the slits 40 and the inclined portions 41 are provided at the end of the fin 33 on the side of the second joint 32, the side of the first joint 31 can be obtained. While the heat transfer performance between the flat tube 20 and the corrugated fins 30 is improved, most of the water droplets attached to the fins 33 can be dropped from the slits 40 to the fins 33 below.

  According to the first embodiment, the water droplets attached to the surface of the corrugated fins 30 are guided to the slit 40, hit the inclined portion 41, guided downward, and dropped from the slit 40 downward. Thus, when draining, an opening part is unnecessary to the 1st joined part 31 and the 2nd joined part 32 to which flat tube 20 and corrugate fin 30 are joined. For this reason, the joint area in the 1st junction part 31 and the 2nd junction part 32 is securable enough. Therefore, drainage can be improved while maintaining the heat transfer performance.

  In addition, when the direction (arrow Y direction) in which the plurality of flat tubes 20 extend is vertical, the inclined portion 41 is inclined downward toward the slit 40 from the first joint portion 31 side or the second joint portion 32 side. It has become. As a result, the water droplets fall from the slit 40 to the lower fin portion 33 along the inclined portion 41 toward the central portion in the short side direction (the arrow X direction). Therefore, the water droplets do not fall to the flat tube 20 side, but fall to the central portion of the lower fin portion 33. Therefore, it is suppressed that a water droplet is hold | maintained between the corrugated fin 30 and the flat tube 20 by surface tension. In addition, the inclined part 41 has a different inclination with respect to the fin surface part 33a continuously from the part below 2 mm from the 1st junction part 31 or the 2nd junction part 32 to the slit 40 continuously.

  Furthermore, the fin portion 33 is inclined downward to the short side direction (the arrow X direction) of the flat tube 20 from the first joint portion 31 to the second joint portion 32, and the inclined portion 41 is the fin portion 33. Are provided on the side of the second joint 32 in FIG. Therefore, the water droplets attached to the fin portion 33 flow from the first bonding portion 31 side to the second bonding portion 32 side, and the inclined portion 41 provided on the second bonding portion 32 side lowers from the slit 40. It falls into the fin section 33.

  Furthermore, the first joint portion 31 and the second joint portion 32 are formed parallel to the long side direction (arrow Y direction) of the flat tube 20, and the inclined portion 41 is long side direction (arrow Y direction). The heights of both ends of) are equal. As described above, even if the heights of both ends of the inclined portion 41 are equal, drainage can be smoothly performed.

  The corrugated fin 30 is a part of the fin portion 33 and closes a portion of the sub slit 50 formed to extend in a direction different from the slit 40, and the sub inclined portion inclined with respect to the other portion of the fin portion 33 And 51. Therefore, the heat transfer performance of the corrugated fins 30 is improved.

Second Embodiment
FIG. 4 is a perspective view showing a heat exchanger 105 according to Embodiment 2 of the present invention. The second embodiment is different from the first embodiment in that a plurality of inclined portions 141 are provided in the long side direction (the arrow Y direction). In the second embodiment, the same parts as those of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. The differences from the first embodiment will be mainly described.

  As shown in FIG. 4, in the fin portion 133, slits 140 cut out so as to extend in the long side direction (arrow Y direction) are provided at both ends in the short side direction (arrow X direction) of the fin portion 133 Three are formed in the long side direction (arrow Y direction). Here, the slit 140 on the upstream side of the flow of air is referred to as a windward slit 140a, the slit 140 on the downstream side of the flow of air is referred to as a windward slit 140c, and the windward slit 140a and the windward slit 140c The slit 140 between them is called an intermediate slit 140b. Note that two slits 140 may be formed, or four or more slits may be formed.

  Further, three inclined portions 141 are formed in the long side direction (arrow Y direction) at both end portions in the short side direction (arrow X direction) of the fin portion 133. Here, the inclined portion 141 on the upstream side of the flow of air is referred to as the windward inclined portion 141a, and the inclined portion 141 on the downstream side of the flow of air is referred to as the windward side inclined portion 141c. The inclined portion 141 between the side inclined portion 141 c and the side inclined portion 141 c will be referred to as an intermediate inclined portion 141 b. In addition, two inclined parts 141 may be provided, and four or more may be provided.

  According to the second embodiment, a plurality of inclined portions 141 are provided in the long side direction (the arrow Y direction) of the flat tube 20. Thus, the water droplets attached to the surface of the corrugated fins 130 are guided to the windward slit 140a, the middle slit 140b and the windward slit 140c, and hit the windward inclined portion 141a, the middle inclined portion 141b and the windward inclined portion 141c, , And falls downward from the windward slit 140a, the middle slit 140b, and the windward slit 140c. Therefore, as in the first embodiment, retention of water droplets between the corrugated fins 130 and the flat tube 20 is suppressed by surface tension. Therefore, the fall of the heat transfer performance by the ventilation resistance increasing by residual water can be suppressed. Further, since a plurality of inclined portions 141 and slits 140 are provided in the long side direction (arrow Y direction), heat is easily transmitted from the flat tube 20 to the corrugated fins 130 by the gap between the slits 140. For this reason, the heat transfer performance of the heat exchanger 105 is improved.

Third Embodiment
FIG. 5 is a perspective view showing a heat exchanger 205 according to Embodiment 3 of the present invention. The third embodiment is different from the second embodiment in that the lengths in the long side direction (the arrow Y direction) of the plurality of inclined portions 241 become shorter from the upstream side to the downstream side in the air flow direction. In the third embodiment, the same parts as those in the first and second embodiments are assigned the same reference numerals and explanations thereof will be omitted, and differences from the first and second embodiments will be mainly described.

  As shown in FIG. 5, in the fin portion 233, slits 240 which are cut out so as to extend in the long side direction (arrow Y direction) are provided at both ends in the short side direction (arrow X direction) of the fin portion 233. Three are formed in the long side direction (arrow Y direction). Here, the slit 240 on the upstream side of the flow of air is referred to as a windward slit 240a, the slit 240 on the downstream side of the flow of air is referred to as a windward slit 240c, and the windward slit 240a and the windward slit 240c The slit 240 in between is called an intermediate slit 240 b. Then, the length in the long side direction (the arrow Y direction) of each slit 240 becomes shorter from the upstream side to the downstream side in the air flow direction. That is, the length of the windward slit 240a in the long side direction (arrow Y direction) is the longest, and the length of the middle slit 240b in the long side direction (arrow Y direction) is the second longest, and the windward side slit 240c is the long side The length (in the direction of the arrow Y) is the shortest. Note that two slits 240 may be formed, or four or more slits may be formed.

  Further, three inclined portions 241 are respectively formed in the long side direction (arrow Y direction) at both end portions in the short side direction (arrow X direction) of the fin portion 233. Here, the upstream inclined portion 241 of the air flow is referred to as a windward inclined portion 241a, and the downstream inclined portion 241 of the air flow is referred to as a windward inclined portion 241c, and the windward inclined portion 241a and the windward. The inclined portion 241 between the side inclined portion 241 c and the side inclined portion 241 c will be referred to as an intermediate inclined portion 241 b. And the length of the long side direction (arrow Y direction) of each inclined portion 241 becomes short from the upstream side to the downstream side in the direction in which the air flows. That is, the length of the windward inclined portion 241a in the long side direction (arrow Y direction) is the longest, and the length of the middle inclined portion 241b in the long side direction (arrow Y direction) is the second longest. The length in the long side direction (arrow Y direction) is the shortest. In addition, two inclined parts 241 may be provided, and four or more may be provided.

  According to the third embodiment, in the plurality of inclined portions 241, the length in the long side direction (the arrow Y direction) of the flat tube 20 becomes shorter from the upstream side to the downstream side in the air flow direction. Generally, in the corrugated fins 230, the amount of air that hits the windward side is larger than the windward side, so the amount of heat exchange with the refrigerant is large. For this reason, when the surface of the flat tube 20 and the corrugated fin 230 is 0 ° C. or less, the amount of frost formed on the surface of the flat tube 20 and the corrugated fin 230 is larger on the windward side than on the downwind side. Therefore, when the defrosting operation is performed, the amount of water to be melted is larger on the upwind side than on the downwind side, so the drain water is increased. Also, when the heat exchanger 205 acts as an evaporator, when air flows to the heat exchanger 205, the surfaces of the flat tubes 20 and the corrugated fins 230 become lower than the temperature of the air. For this reason, water vapor in the air condenses on the surfaces of the flat tubes 20 and the corrugated fins 230. At this time, since the amount of heat exchange with the refrigerant is larger on the windward side than on the windward side, the amount of generated condensed water is large.

  In the third embodiment, since the length in the long side direction (the direction of the arrow Y) of the plurality of inclined portions 241 is longer on the windward side than on the windward side, water droplets adhering more on the windward side are drained. Can. As described above, the lengths of the plurality of inclined portions 241 provided in the long side direction (arrow Y direction) correspond to the distribution of the amount of water droplets in the long side direction (arrow Y direction). Because of this, drainage can be further improved.

Fourth Embodiment
FIG. 6 is a perspective view showing a heat exchanger 305 according to Embodiment 4 of the present invention. The fourth embodiment is different from the second embodiment in that the lengths in the short side direction (the arrow X direction) of the plurality of inclined portions 341 become shorter from the upstream side to the downstream side in the air flow direction. In the fourth embodiment, the same parts as in the first, second and third embodiments are given the same reference numerals, and the description thereof is omitted, and the differences from the first, second and third embodiments will be mainly described.

  As shown in FIG. 6, in the fin portion 333, slits 340 cut out so as to extend in the long side direction (arrow Y direction) are provided at both ends in the short side direction (arrow X direction) of the fin portion 333 Three are formed in the long side direction (arrow Y direction). Here, the slit 340 on the upstream side of the flow of air is referred to as a windward slit 340a, the slit 340 on the downstream side of the flow of air is referred to as a windward slit 340c, and the windward slit 340a and the windward slit 340c The slit 340 between them is called an intermediate slit 340b. And the length of the short side direction (arrow X direction) of each slit 340 becomes short from the upstream side to the downstream side of the direction through which air flows. That is, the length of the windward slit 340a in the short side direction (arrow X direction) is the longest, and the length of the middle slit 340b in the short side direction (arrow X direction) is the second longest, and the short side direction of the windward slit 340c The length (in the direction of the arrow X) is the shortest. In addition, two slits 340 may be formed, or four or more slits may be formed.

  Further, three inclined portions 341 are respectively formed in the long side direction (arrow Y direction) at both end portions in the short side direction (arrow X direction) of the fin portion 333. Here, the upstream inclined portion 341 of the air flow is referred to as a windward inclined portion 341a, and the downstream inclined portion 341 of the air flow is referred to as a windward inclined portion 341c, and the windward inclined portion 341a and the windward. The inclined portion 341 between the side inclined portion 341 c and the side inclined portion 341 c will be referred to as an intermediate inclined portion 341 b. And the length of the short side direction (arrow X direction) of each inclined portion 341 becomes short from the upstream side to the downstream side in the air flow direction. That is, the length of the upwind side inclined portion 341a in the short side direction (arrow X direction) is the longest, and the length of the short side direction (arrow X direction) of the middle inclined portion 341b is the second longest The length in the short side direction (arrow X direction) is the shortest. In addition, two inclined parts 341 may be provided, and four or more may be provided.

  According to the fourth embodiment, in the plurality of inclined portions 341, the length in the short side direction (the arrow X direction) of the flat tube 20 becomes shorter from the upstream side to the downstream side in the air flow direction. Generally, in the corrugated fins 330, the amount of air hitting the windward side is larger than the windward side, so the amount of heat exchange with the refrigerant is large. For this reason, when the surface of the flat tube 20 and the corrugated fin 330 becomes 0 ° C. or less, the amount of frost formed on the surface of the flat tube 20 and the corrugated fin 330 is larger on the windward side than on the downwind side. Therefore, when the defrosting operation is performed, the amount of water to be melted is larger on the upwind side than on the downwind side, so the drain water is increased. Also, when the heat exchanger 305 acts as an evaporator, when air flows to the heat exchanger 305, the surfaces of the flat tube 20 and the corrugated fins 330 become lower than the temperature of the air. For this reason, water vapor in the air condenses on the surfaces of the flat tubes 20 and the corrugated fins 330. At this time, since the amount of heat exchange with the refrigerant is larger on the windward side than on the windward side, the amount of generated condensed water is large.

  In the fourth embodiment, since the length in the short side direction (arrow X direction) of the flat tubes 20 of the plurality of inclined portions 341 is longer on the windward side than on the windward side, water droplets attached more on the windward side Can drain water. Thus, the lengths in the short side direction (arrow X direction) of the plurality of inclined portions 341 provided in the long side direction (arrow Y direction) correspond to the distribution of the amount of water droplets in the long side direction (arrow Y direction) Because of this, drainage can be further improved.

  In the plurality of inclined portions 341 provided in the long side direction (arrow Y direction), the length in the long side direction (arrow Y direction) becomes shorter from the upstream side to the downstream side in the air flow direction, The length in the short side direction (arrow X direction) may be made shorter from the upstream side to the downstream side in the air flow direction. In this case, even in the case where the water droplets adhere more significantly to the windward side than to the windward side in the fin portion 333, drainage performance can be improved.

Embodiment 5
FIG. 7 is a perspective view showing a heat exchanger 405 according to Embodiment 5 of the present invention. The fifth embodiment is different from the second embodiment in that the sub slit 450 is inclined with respect to the short side direction (the arrow X direction). In the fifth embodiment, the same parts as in the first, second, and third embodiments are given the same reference numerals, and the description thereof is omitted, and the differences from the first, second, third and fourth embodiments are mainly described. Explain to.

  As shown in FIG. 7, in the sub slit 450, the short side direction (the arrow X direction) in the fin portion 433 so that the first bonding portion 31 side is upwind and the second bonding portion 32 side is downwind. It is inclined against. Further, the sub-inclined portion 451 is inclined with respect to the short side direction (the arrow X direction) so that the first bonding portion 31 side is upwind and the second bonding portion 32 side is downwind in the fin portion 433. ing. The height of the sub-inclined portion 451 is higher on the upstream side in the air flow direction than on the downstream side.

  According to the fifth embodiment, the sub slit 450 is inclined with respect to the short side direction (the arrow X direction) of the flat tube 20, and the height of the sub inclined portion 451 is on the upstream side in the air flow direction. Is higher than downstream. Generally, in the corrugated fins 430, the amount of air hitting the windward side is larger than the windward side, so the amount of heat exchange with the refrigerant is large. Therefore, when the surface of the flat tube 20 and the corrugated fin 430 is 0 ° C. or less, the amount of frost formed on the surface of the flat tube 20 and the corrugated fin 430 is larger on the windward side than on the downwind side. Therefore, when the defrosting operation is performed, the amount of water to be melted is larger on the upwind side than on the downwind side, so the drain water is increased. Also, when the heat exchanger 405 acts as an evaporator, when the air flows to the heat exchanger 405, the surfaces of the flat tubes 20 and the corrugated fins 430 become lower than the temperature of the air. For this reason, water vapor in the air condenses on the surfaces of the flat tube 20 and the corrugated fins 430. At this time, since the amount of heat exchange with the refrigerant is larger on the windward side than on the windward side, the amount of generated condensed water is large.

  In the fifth embodiment, since the height of the sub-inclined portion 451 is higher on the upstream side in the air flow direction than on the downstream side, the air is blown by the outdoor blower 8 to adhere to the sub-inclined portion 451 The water droplets flow from the upwind side to the downwind side. As a result, since the water droplets largely biased to the windward side are guided to the windward side, the water droplets are dispersed in the long side direction (arrow Y direction) in the fin portion 433. For this reason, the distribution of water droplets in the long side direction (arrow Y direction) in the fin portion 433 is made uniform, and the drainage performance for discharging water is improved.

Sixth Embodiment
FIG. 8 is a perspective view showing a heat exchanger 505 according to Embodiment 6 of the present invention. In the sixth embodiment, the fin portion 533 is parallel to the short side direction (arrow X direction), and the sub-inclination portion 551 is inclined toward the center of the short side direction (arrow X direction) in the fin portion 533. The second embodiment differs from the first to fifth embodiments in that In the sixth embodiment, the same parts as in the first, second, third, and fourth embodiments are assigned the same reference numerals, and the descriptions thereof are omitted. The differences will be mainly described.

  As shown in FIG. 8, the fin portion 533 is provided parallel to the short side direction (the arrow X direction), that is, horizontally. As a result, the number of fin portions 533 increases in the gravity direction, and the fin portions 533 can be mounted with high density. Therefore, the heat transfer area is increased and the heat transfer performance is increased. Further, a plurality of sub slits 550 are formed in two sets in the long side direction (arrow Y direction), with the center of the short side direction (arrow X direction) of the fin portion 533 being symmetrical. One set of the sub-slits 550 is formed such that one end is on the side of the first joint 31 and on the upwind side, and the other end is on the side of the second joint 32 and on the downwind side. The other set of sub-slits 550 is formed such that one end is on the second joint 32 side and upwind, and the other end is the first joint 31 and downwind.

  A plurality of sub-inclined portions 551 are formed in two sets in the long side direction (arrow Y direction), with the center of the fin portion 533 in the short side direction (arrow X direction) symmetrical. One set of the secondary inclined portions 551 is formed such that one end is on the first joint 31 side and is upwind, and the other end is on the second joint 32 side and is leeward. The other set of sub-inclined portions 551 is formed such that one end is on the second joint 32 side and upwind and the other end is on the first joint 31 and downwind. Since the fin portion 533 is provided parallel to the short side direction (arrow X direction), the water droplets attached to the fin portion 533 are unlikely to flow to the first bonding portion 31 side and the second bonding portion 32 side. . In the sixth embodiment, since the sub slit 550 and the sub inclined portion 551 are formed symmetrically with respect to the center in the short side direction (the arrow X direction) of the fin portion 533, the fins blown by the air blown by the outdoor blower 8 The water droplets are uniformly dropped from the sub-slit 550 as the water droplets are guided from the center to both ends in the short side direction (arrow X direction) of the portion 533. This improves drainage performance. Further, the sub-inclined portion 51 is inclined toward the center in the short side direction (arrow X direction) in the fin portion 533.

  According to the sixth embodiment, sub slit 550 is inclined with respect to the short side direction (the arrow X direction) of flat tube 20, and sub inclined portion 551 is the short side direction in fin portion 533 (the arrow X direction). It inclines toward the center of). Thereby, the water droplets fall from the sub slit 550 to the lower fin portion 533 toward the central portion in the short side direction (the arrow X direction) along the sub inclined portion 551. Therefore, the water droplets do not fall to the flat tube 20 side, but fall to the central portion of the lower fin portion 33. Therefore, it is suppressed that a water droplet is hold | maintained between the corrugated fin 530 and the flat tube 20 by surface tension.

Embodiment 7
FIG. 9 is a perspective view showing a heat exchanger 605 according to Embodiment 7 of the present invention. The seventh embodiment is different from the first to sixth embodiments in that the inclined portions are a pair of facing inclined portions 641 facing each other. In the sixth embodiment, the same parts as those in the first, second, third, fourth, and fifth embodiments are given the same reference numerals, and the description thereof is omitted. And 6 will be mainly described.

  As shown in FIG. 9, one slit 640 is formed on the entire surface of the fin portion 633. The pair of facing inclined portions 641 are both inclined toward the center of the fin portion 633 in the short side direction (the arrow X direction). The pair of facing inclined portions 641 are both bent starting from the bent portion 634 of the fin portion 633. In addition, the bending part 634 is in the position of 2 mm or less from the flat tube 20. Further, the facing inclined portion 641 is provided with a heat exchange promoting portion 635 which protrudes upward from the facing inclined portion 641 and increases the heat transfer area to promote the heat exchange between the air and the refrigerant. The heat exchange promoting portion 635 is not limited to the unevenness, and may be a louver, a cut and raise, or the like.

  Furthermore, the four corners of the slit 640 and both ends of the bent portion 634 are not perpendicular but inclined, and a reinforced bent portion 636 is provided to suppress generation of cracks from both ends of the bent portion 634. . Thereby, the strength of the corrugated fins 630 is improved, and the assemblability and the manufacturability of the heat exchanger 605 are improved. The reinforcing bent portion 636 is inclined with respect to the short side direction (the arrow X direction). The reinforcing bent portion 636 may have an arc shape.

  According to the seventh embodiment, the inclined portions are a pair of facing inclined portions 641 which are provided to close a part of one slit 640 and face each other. Therefore, the facing inclined portion 641 itself is a portion where heat exchange mainly takes place in the corrugated fin 630. For this reason, drainage property can be improved, maintaining heat transfer performance more.

  Reference Signs List 1 air conditioner, 2 refrigerant circuit, 3 compressor, 4 flow path switching unit, 5 heat exchanger, 6 expansion unit, 7 indoor heat exchanger, 8 outdoor fan, 9 indoor fan, 20 flat tube, 20a flat surface, Reference Signs List 21 refrigerant flow path, 30 corrugated fins, 31 first joint portion, 32 second joint portion, 33 fin portion, 33 a fin surface portion, 40 slits, 40 a upstream slit, 40 b downstream slit, 41 inclined portion, 41 a upstream Side inclined part, 41b downstream side inclined part, 50 sub slit, 51 sub inclined part, 105 heat exchanger, 130 corrugated fin, 133 fin part, 140 slit, 140a windward slit, 140b middle slit, 140c windward slit, 141 Inclined part, 141a upwind inclined part, 141b middle inclined part, 141c downwind inclined part, 205 heat exchange , 230 corrugated fins, 233 fins, 240 slits, 240a upwind slits, 240b middle slits, 240c downwind slits, 241 inclines, 241a upwind inclines, 241b middle inclines, 241c downwind inclines, 305 heat Exchanger, 330 corrugated fins, 333 fins, 340 slits, 340a upwind slits, 340b middle slits, 340c downwind slits, 341 slopes, 341a upwind slopes, 341b middle inclines, 341c downwind slopes, 405 Heat exchanger, 430 corrugated fin, 433 fin portion, 450 sub slit, 451 sub inclined portion, 505 heat exchanger, 530 corrugated fin, 533 fin portion, 550 sub slit, 551 sub inclined portion, 605 heat exchanger 630 corrugated fins 633 fin unit, 634 bent portion, 635 the heat exchange facilitating unit, 636 reinforcing bent portion, 640 slit, 641 facing the inclined portion.

Claims (9)

A plurality of flat tubes arranged at intervals such that the flat surfaces thereof are parallel;
Corrugated fins sandwiched between one adjacent flat tube and the other flat tube adjacent to the plurality of flat tubes;
The corrugated fin is
A first joint portion joined to the flat surface of the one flat tube at one convex portion of the corrugated shape;
A second joint portion joined to the flat surface of the other flat tube at the other convex portion of the corrugated shape;
A fin portion that exchanges heat with air between the first joint portion and the second joint portion;
The fin portion is
A fin surface connecting the first joint and the second joint;
A slit opened longitudinally in the direction along the flat surface between the first joint and the second joint;
And an inclined portion having a different inclination with respect to the fin surface portion continuously from the vicinity of the first joint portion or the second joint portion to the slit;
When the extending direction of the plurality of flat tubes is vertical, the inclined portion is inclined downward toward the slit from the first joint portion side or the second joint portion side ,
The inclined portion is
A plurality of the flat tubes are provided in the long side direction of the flat tube,
The plurality of inclined portions are
The heat exchanger whose length in the long side direction of the flat tube becomes short from the upstream side to the downstream side in the direction of air flow . The plurality of inclined portions are
The short side direction of the length of the heat exchanger of the shorter becomes claim 1, wherein from the upstream side to the downstream side of the air flow direction of the flat tubes. A plurality of flat tubes arranged at intervals such that the flat surfaces thereof are parallel;
Corrugated fins sandwiched between one adjacent flat tube and the other flat tube adjacent to the plurality of flat tubes;
The corrugated fin is
A first joint portion joined to the flat surface of the one flat tube at one convex portion of the corrugated shape;
A second joint portion joined to the flat surface of the other flat tube at the other convex portion of the corrugated shape;
A fin portion that exchanges heat with air between the first joint portion and the second joint portion;
The fin portion is
A fin surface connecting the first joint and the second joint;
A slit opened longitudinally in the direction along the flat surface between the first joint and the second joint;
And an inclined portion having a different inclination with respect to the fin surface portion continuously from the vicinity of the first joint portion or the second joint portion to the slit;
When the extending direction of the plurality of flat tubes is vertical, the inclined portion is inclined downward toward the slit from the first joint portion side or the second joint portion side ,
The corrugated fin is
A part of the sub-slit which is a part of the fin and is formed to extend in a direction different from the slit is closed, and the sub-slit further includes a sub-slope inclined with respect to the other part of the fin
The sub slit is
Inclined to the short side direction of the flat tube,
The height of the sub-slope is
A heat exchanger whose upstream side in the air flow direction is higher than its downstream side . The sub slit is
Inclined to the short side direction of the flat tube,
The secondary inclined portion is
The heat exchanger according to claim 3 , wherein the heat exchanger is inclined toward the center in the direction of the short side of the flat tube in the fin portion. The inclined portion is
Any of the first joint portion and the second 2 2 mm following parts from the junction of the claims 1-4 and has a continuously different inclination with respect to the fin surface until the slit 1 The heat exchanger according to the item . The inclined portion is
The heat exchanger according to any one of claims 1 to 5, which is a pair of facing inclined portions which are provided so as to close a part of one slit and which face each other. The fin portion is
From the first joint to the second joint, it is inclined downward with respect to the short side direction of the flat tube,
The inclined portion is
The heat exchanger according to any one of claims 1 to 6 , provided on the side of the second joint portion in the fin portion. The first joint and the second joint are:
The flat tube is formed parallel to the long side direction of the flat tube,
The inclined portion is
The heat exchanger according to any one of claims 1 to 7 , wherein the heights of both ends in the direction of the long side of the flat tube are equal. The heat exchanger according to any one of claims 1 to 8 , wherein the surface of the corrugated fin is hydrophilic.

Images