JPWO2018073898A1 - Heat exchanger, outdoor unit, and apparatus and method for manufacturing heat exchanger - Google Patents

Abstract

The heat exchanger includes: a first heat exchange unit having a plurality of heat transfer tubes arranged in one direction through which a working fluid flows, and a plurality of fins connected to the plurality of heat transfer tubes and arranged in the other direction; A plurality of heat transfer tubes and a plurality of fins, and the first heat exchange unit includes a second heat exchange unit bent so that the arrangement direction of the fins is different from that of the first heat exchange unit; The direction is inclined with respect to the arrangement direction of the heat transfer tubes in the first heat exchange unit.

Description

  The present invention relates to a heat exchanger and an outdoor unit provided with the heat exchanger, and an apparatus and method for manufacturing the heat exchanger.

  In the indoor unit, there is disclosed a multi-pyramidal cylindrical heat exchanger erected in a casing so as to surround the outer peripheral side of the centrifugal fan (see, for example, Patent Document 1). The heat exchanger of Patent Document 1 has a configuration in which the heat transfer portion is disposed in an inclined manner in the ventilation passage in order to reduce the ventilation resistance and improve the heat exchange efficiency.

JP, 2001-304607, A

  By the way, in the outdoor unit, unlike the indoor unit of Patent Document 1 described above, drainage from the heat exchanger is particularly important. In general, when frost forms on the heat exchanger, the frost resistance increases the ventilation resistance, and the air volume decreases to lower the heat exchange performance. For example, there is a problem that condensed water frozen between the heat transfer pipe and the heat transfer pipe is likely to frost. Further, frost formation in the heat exchanger may cause a decrease in heating capacity (particularly heating low temperature capacity). Furthermore, in the case of a heat exchanger in which heat transfer tubes are arranged substantially in the vertical direction, condensed water and molten water and the like drained from the upper heat transfer tubes may accumulate in the lower heat transfer tubes.

  The present invention has been made to solve the problems as described above, and it is an object of the present invention to provide a heat exchanger and an outdoor unit for suppressing frost formation, and an apparatus and a method for manufacturing the heat exchanger.

  A heat exchanger according to the present invention includes a plurality of heat transfer tubes arranged in one direction through which a working fluid flows, and a plurality of fins connected to the plurality of heat transfer pipes and arranged in the other direction. A heat exchange unit, a plurality of the heat transfer tubes, and a plurality of fins, the second heat exchange unit being bent such that the arrangement direction of the fins is different from the first heat exchange unit; The arrangement direction of the heat transfer tubes in the second heat exchange portion is inclined with respect to the arrangement direction of the heat transfer tubes in the first heat exchange portion.

  According to the heat exchanger of the present invention, since the arrangement direction of the heat transfer tubes in the second heat exchange unit is inclined to the arrangement direction of the heat transfer tubes in the first heat exchange unit, the first heat exchange unit and the second heat exchange unit At least one of the heat exchange parts is in a state of being inclined from the vertical direction. Therefore, dew condensation water or the like generated in the heat transfer tube whose alignment direction is inclined slides to the end of the heat transfer tube and moves or drops downward from the end of the heat transfer tube. Since the drainage of the heat exchanger is improved by this, the heat exchanger can suppress frost formation.

It is a side view which shows schematic structure of the outdoor unit of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a schematic block diagram before the bending process of the heat exchanger which concerns on Embodiment 1 of this invention. It is a schematic diagram which shows the lower part periphery of the heat exchanger of FIG. It is a schematic plan view which shows the manufacturing apparatus of the heat exchanger which concerns on Embodiment 1 of this invention. It is AA sectional drawing of FIG. 4A which shows the state before the bending process of a heat exchanger. It is sectional drawing which shows the state after the bending process of the heat exchanger of FIG. 4B. It is a block diagram of the outdoor unit of the air conditioning apparatus which concerns on Embodiment 2 of this invention. It is a partial block diagram of the heat exchanger which concerns on Embodiment 3 of this invention. It is a partial block diagram of the heat exchanger which concerns on Embodiment 5 of this invention. It is a partial block diagram of the heat exchanger which concerns on Embodiment 6 of this invention. It is a partial block diagram of the heat exchanger which concerns on Embodiment 7 of this invention. It is a partial block diagram of the heat exchanger which concerns on Embodiment 8 of this invention.

Embodiment 1
FIG. 1 is a side view showing a schematic configuration of an outdoor unit of an air conditioning apparatus according to Embodiment 1 of the present invention. FIG. 2 is a schematic configuration view of the heat exchanger according to Embodiment 1 of the present invention before bending. The outdoor unit 10 shown in FIG. 1 includes a housing 9, a fan 3 installed in the housing 9, and the heat exchanger 1 on the heat source side. Furthermore, although not shown, the outdoor unit 10 is provided with a compressor that supplies the working fluid, and a switching device that switches between the cooling operation and the heating operation. The fan 3 is configured of, for example, a propeller fan, and supplies a necessary amount of air to the heat exchanger 1. The fan 3 is disposed, for example, in front of the heat exchanger 1 in the front-rear direction (the arrow X direction) of the outdoor unit 10. As the working fluid, for example, a refrigerant which is said not to destroy the ozone layer may be used. For example, the working fluid is an HFC refrigerant, an HFO refrigerant, or a mixed refrigerant of an HFC refrigerant and an HFO refrigerant.

  The heat exchanger 1 is, for example, a fin-tube type heat exchanger, and performs heat exchange between the working fluid and the air supplied by the fan 3. The heat exchanger 1 functions as an evaporator during heating operation of the air conditioner, and functions as a condenser during cooling operation or defrosting operation.

  The heat exchanger 1 has an L shape in a plan view, and is disposed so as to face the back surface of the casing 9 and the flat plate-shaped first heat exchanging portion 1 a disposed facing the side surface of the casing 9 And a second heat exchange section 1b in the form of a flat plate. In addition, the corner part 1c (refer FIG. 4C) which is a boundary part of the 1st heat exchange part 1a and the 2nd heat exchange part 1b forms the smooth angle | corner. The corner 1 c may be provided, for example, with a constant curvature from the bottom to the top.

  The first heat exchange unit 1a includes a plurality of heat transfer tubes 2 arranged in one direction, and a plurality of fins 4 or the like arranged in the other direction. The fins 4 are formed in a flat plate shape, and a plurality of through holes or notches for mounting the plurality of heat transfer tubes 2 are provided along the longitudinal direction. The heat transfer tube 2 is formed of, for example, a heat transfer tube having a flat surface such as a circular tube or a flat tube. FIG. 1 shows the case where the heat transfer tube 2 is a flat tube. The flat tube may be a flat multi-hole tube formed so that a plurality of refrigerant channels are divided, or may be a flat tube in which one refrigerant channel is formed. The second heat exchange unit 1b has a plurality of heat transfer pipes 2 and a plurality of fins 4 as in the first heat exchange unit 1a, but is bent with respect to the first heat exchange unit 1a. The arrangement direction of the fins 4 of the second heat exchange unit 1b is different from the arrangement direction of the fins 4 of the first heat exchange unit 1a, and the first heat exchange unit 1a and the second heat exchange unit 1b have, for example, 90 °. Have an angle of

  In the first heat exchange portion 1a and the second heat exchange portion 1b, the plurality of fins 4 are joined to the plurality of heat transfer tubes 2 such that the crossing angle with the plurality of heat transfer tubes 2 is a constant angle (for example, 90 °) It is done. The heat transfer tubes 2 in the same row are formed by bending a single heat transfer tube. Further, the arrangement direction 31b of the heat transfer tubes 2 in the second heat exchange unit 1b is configured to be inclined with respect to the arrangement direction 31a of the heat transfer tubes 2 in the first heat exchange unit 1a.

  Here, the arrangement direction 31a of the heat transfer tubes 2 of the first heat exchange unit 1a is inclined at an angle θ with respect to the arrangement direction 31b of the heat transfer tubes 2 of the second heat exchange unit 1b. In the heat exchanger 100 shown in FIG. 2, for example, each heat transfer tube 2 is inserted into a through hole or a notch formed in each fin 4, and welding is performed so that the outer periphery of the heat transfer tube 2 contacts the fins 4. It is joined. The heat exchanger 1 shown in FIG. 1 can be formed, for example, from a flat plate-like heat exchanger 100 shown in FIG.

  Bending is performed along a bending position L1 which is inclined by an angle θ with respect to the arrangement direction 31 of the heat transfer tubes 2 of the flat heat exchanger 100. For example, when the bending position L1 is set to be inclined in the R1 direction shown in FIG. 2, the length of the upper portion of the portion to be the first heat exchange portion 1a is longer than that of the bottom portion 100e and the portion to be the second heat exchange portion 1b Is shorter at the top than the bottom 100e. And bending position L1 turns into corner 1c. Note that the angle θ may be determined based on, for example, a falling angle of dew condensation water, a ventilation resistance, or the like.

  The heat exchanger 1 is installed on the bottom plate 6 of the housing 9. At this time, the arrangement direction 31a of the heat transfer tubes 2 of the first heat exchange unit 1a and the arrangement direction 31b of the heat transfer tubes of the second heat exchange unit 1b are both inclined with respect to the vertical direction (arrow Z direction). In the second heat exchange unit 1 b, the upper side of the second heat exchange unit 1 b is inclined to the back of the housing 9 from the lower side in the vertical direction (the arrow Z direction) of the outdoor unit 10. Condensed water or the like generated in the second heat exchange portion 1b is drained along a sliding direction 11 indicated by an arrow in FIG. Specifically, condensed water or the like of the heat transfer pipe 2 slides the outer periphery of the heat transfer pipe 2 toward the back side of the housing 9, and the bottom end 9 a of the housing 9 at the rear end of the heat transfer pipe 2 Drop toward the bottom or move downward along the fins 4. On the other hand, the lower side of the first heat exchanger 1a is inclined to the inside of the outdoor unit 10 from the upper side. Therefore, dew condensation water or the like generated in the first heat exchange portion 1 a slides toward the inside of the outdoor unit 10 and falls toward the bottom surface 9 a of the housing 9 at the front end of the heat transfer tube 2 or Move down along the fin 4.

  FIG. 3 is a schematic view showing the lower periphery of the heat exchanger of FIG. The outdoor unit 10 of FIG. 3 has a shock absorbing material 5 between the second heat exchange unit 1 b and the bottom plate 6. The cushioning material 5 is made of, for example, an insulating material that electrically insulates the second heat exchange portion 1 b and the bottom plate 6. The shock absorbing material 5 has the inclined surface 5a which inclined the angle (theta), and the bottom part 1e of the 2nd heat exchange part 1b contacts on the inclined surface 5a.

  In the heat exchanger 1 shown in FIG. 1, when one of the first heat exchange portion 1 a and the second heat exchange portion 1 b is inclined to the housing 9 side, the other is inclined to the inside of the housing 9. Therefore, the cushioning material 5 is disposed in the lower part of the second heat exchange portion 1b which is inclined backward so that the height of the inclined surface 5a is lowered toward the back side of the housing 9. On the other hand, the cushioning material 5 is disposed in the lower part of the first heat exchange portion 1a which is inclined forward so that the height of the inclined surface 5a is increased toward the side surface side of the housing 9. As described above, the shock absorber 5 is provided between the heat exchanger 1 and the bottom plate 6 so that the heat exchanger 1 can be stably installed in the outdoor unit 10.

(Production equipment for heat exchangers)
FIG. 4A is a schematic plan view showing the apparatus for manufacturing a heat exchanger according to Embodiment 1 of the present invention. FIG. 4B is a cross-sectional view taken along line A-A of FIG. 4A showing the heat exchanger before bending. FIG. 4C is a cross-sectional view showing the heat exchanger of FIG. 4B after bending.

  The manufacturing apparatus 20 of the heat exchanger 1 is configured of a bending jig 21, a stopper jig 22, a bending die 23 and the like. The bending jig 21 includes, for example, a fixed portion 21 b and a movable portion 21 a disposed with a gap between the fixed portion 21 b and the fixed portion 21 b. A movable shaft 21c is provided on the fixed portion 21b side of the movable portion 21a, and rotates toward the fixed portion 21b around the movable shaft 21c.

  The stop jig 22 determines the position and the orientation of the flat heat exchanger 100 with respect to the bending jig 21. Further, the stopper jig 22 is configured of, for example, a first stopper jig 22a that supports the side surface 100d of the heat exchanger 100, and a second stopper jig 22b that supports the bottom portion 100e. The first stopper jig 22a and the second stopper jig 22b have, for example, a right triangle shape. The first stopper jig 22a is fixed to the movable portion 21a by a screw or the like so that the surface supporting the side surface 100d is inclined by an angle θ with respect to the movable shaft 21c of the movable portion 21a. The second stopper jig 22b is fixed to the fixed portion 21b by a screw or the like so that the surface supporting the bottom portion 100e is inclined at an angle θ with respect to the vertical direction of the movable shaft 21c.

  The bending die 23 is disposed at a position facing the bending jig 21 with the heat exchanger 100 interposed therebetween, and fixes the heat exchanger 100 positioned by the stopper jig 22 to the bending jig 21. The bending die 23 is formed in a columnar shape, and as shown in FIGS. 4B and 4C, for example, has a cross-sectional water droplet shape. That is, the bending die 23 extends in a circular arc from the straight portion 23a which is a supporting point against the flat heat exchanger 100 at the time of bending, and a guide portion 23b which becomes a guide of the heat exchanger 100 at the time of bending And.

(Production method)
At the time of bending, the heat exchanger 100 is first installed in the bending jig 21. At this time, the side surface 100d is supported by the oblique side portion of the first stopper jig 22a, and the bottom 100e is supported by the oblique side portion of the second stopper jig 22b, whereby the bending position L1 is arranged along the movable shaft 21c. . That is, as shown in FIG. 4A, the heat exchanger 100 is installed in the bending jig 21 in a state where the arrangement direction 31 of the heat transfer tubes 2 is inclined at an angle θ in the R2 direction from the movable shaft 21c. The bending die 23 is disposed on the heat exchanger 100 along the gap between the first stopper jig 22a and the second stopper jig 22b. At this time, the top of the water droplet shape of the bending die 23 is disposed on the fixed portion 21 b side, and the guide portion 23 b is disposed on the movable portion 21 a side.

  Then, in a state where the heat exchanger 100 is held down by the bending jig 21 by the bending die 23, the heat exchanger 100 is rotated about the movable shaft 21c in the bending direction 24 as shown in FIG. 4C. The corner portion 1c is formed by being bent along the curved outer periphery of the guide portion 23b. Since the heat exchanger 100 is bent at the bending position L1 inclined from the arrangement direction 31 of the heat transfer tubes 2, each heat transfer tube 2 is twisted when it is bent, and the first heat exchange portion where the arrangement directions of the heat transfer tubes 2 are different from each other 1a and the 2nd heat exchange part 1b are formed. In addition, since spring back occurs in bending of metal, for example, a predetermined bending angle can be realized by bending more than a predetermined bending angle.

  In the first embodiment, the heat exchanger 1 includes a plurality of heat transfer tubes 2 arranged in one direction through which the working fluid flows and a plurality of fins 4 joined to the plurality of heat transfer tubes 2 and arranged in the other direction. And a plurality of heat transfer pipes 2 and a plurality of fins 4, and the second heat exchange section bent so that the arrangement direction of the fins 4 is different from that of the first heat exchange section 1 a The arrangement direction 31b of the heat transfer tubes 2 in the second heat exchange unit 1b is inclined with respect to the arrangement direction 31a of the heat transfer tubes 2 in the first heat exchange unit 1a.

  Accordingly, when the heat exchanger 1 is installed in the outdoor unit 10, at least one of the array direction 31a and the array direction 31b is inclined, so drainage from the heat transfer tube 2 is promoted and frost formation is suppressed. it can. Specifically, condensation water or the like moved from the upper heat transfer pipe 2 is prevented from being accumulated in the lower heat transfer pipe 2. Generally, in the heat exchanger of the outdoor unit, dew condensation water is generated during heating operation, and the frost melts out during the defrosting operation to generate moisture, but the heat exchanger 1 can quickly discharge such moisture. As a result, the defrosting operation time can be shortened, and the rising of the heating performance in the next operation can be improved.

  Further, in the heat exchanger 1, the first heat exchange portion 1a and the second heat exchange portion 1b are integrally configured, and a corner portion which is a boundary portion between the first heat exchange portion 1a and the second heat exchange portion 1b. 1c has a constant curvature from the bottom 1e to the top. From this, the corner portion 1c can be formed from the flat plate-like heat exchanger 100 by bending once using a columnar bending die or the like. Therefore, the manufacturing apparatus 20 of the heat exchanger 1 may be a manufacturing apparatus for manufacturing the L-shaped heat exchanger provided that the first stopper jig 22a and the second stopper jig 22b are provided. It is possible to manufacture the heat exchanger 1 in which frost formation is more suppressed.

  Further, the heat transfer tube 2 is a flat tube. From this, the flat surface of the heat transfer tube 2 is inclined, and condensed water etc. slide on the flat surface and is discharged from the heat exchanger 1. Therefore, the heat exchanger 1 can improve the heat exchange efficiency as compared with the case where a circular pipe is used, and can suppress the formation and the growth of frost which is a concern in the flat pipe.

  Moreover, the bottom part 1e of the 1st heat exchange part 1a is further equipped with the shock absorbing material 5 which has the inclined surface 5a according to the inclination of the arrangement direction 31a of the heat transfer tube 2 in the 1st heat exchange part 1a. Thus, even if the case 9 is installed with the arrangement direction 31a inclined in the housing 9, the gap between the bottom portion 1e of the first heat exchange portion 1a and the bottom plate 6 is stably filled with the buffer material 5. It can be installed. Moreover, since the shock absorbing material 5 is provided with the inclined surface 5a, the shock absorbing material 5 can be inserted into the gap from the side without raising the first heat exchange portion 1a in the height direction.

  Moreover, the bottom part 1e of the 2nd heat exchange part 1b is further equipped with the shock absorbing material 5 which has the inclined surface 5a according to the inclination of the arrangement direction 31b of the heat transfer tube 2 in the 2nd heat exchange part 1b. As a result, even in the case where the arrangement direction 31b is installed in the housing 9 in a state where the arrangement direction 31b is inclined, the buffer material 5 can be stably installed. Moreover, since the shock absorbing material 5 is provided with the inclined surface 5a, the shock absorbing material 5 can be inserted into the gap without lifting the second heat exchange portion 1b.

  Moreover, the shock absorbing material 5 is comprised with the insulating material electrically insulated. Thus, when the heat exchanger 1 is installed on the bottom plate 6 of the outdoor unit 10 or the like, the buffer material 5 can suppress corrosion such as electrolytic corrosion that occurs between dissimilar metals of the heat exchanger 1 and the bottom plate 6.

  The outdoor unit 10 further includes a housing 9 and a heat exchanger 1. Since outdoor unit 10 is equipped with heat exchanger 1 which controlled frost formation from this, heating capability (especially heating low temperature capability) is securable at the time of heating operation.

  Further, in the outdoor unit 10, in the casing 9, the first heat exchange unit 1a faces the side surface of the casing 9 and the second heat exchange unit 1b faces the rear surface of the casing 9 in the casing 9. The arrangement direction 31 b of the heat transfer tubes 2 in the second heat exchange section 1 b is inclined to the back side of the housing 9. As a result, the heat exchanger 1 is installed in the outdoor unit 10, and the second heat exchange unit 1b is inclined backward, so that condensation water and the like generated in the heat exchanger 1 can be discharged to the housing 9 side. Therefore, it can suppress that the drainage from the heat exchanger 1 is splashed on the apparatus inside the housing | casing 9, and the like.

  In the outdoor unit 10, the working fluid is an HFC refrigerant, an HFO refrigerant, or a mixed refrigerant of an HFC refrigerant and an HFO refrigerant. From this, also in the outdoor unit 10 using these refrigerants that are considered not to destroy the ozone layer, the heat exchanger 1 suppresses frost formation and secures the heating capacity (particularly heating low-temperature capacity) during heating operation. Can.

  In addition, the manufacturing apparatus 20 of the heat exchanger 1 has the fixed portion 21 b and the movable portion 21 a which is disposed with a gap between the fixed portion 21 b and rotates toward the fixed portion 21 b about the movable shaft 21 c. And the flat plate-like heat exchanger 100 having the plurality of heat transfer pipes 2 and the plurality of fins 4 installed, and the flat plate-like heat exchange provided on the bending jig 21 and installed on the bending jig 21. A jig 22 supporting the heat exchanger 100 so that the arrangement direction 31 of the heat transfer tubes 2 is inclined with respect to the movable shaft 21c, and a position facing the bending jig 21 across the heat exchanger 1 And a bending die 23 having a curved outer periphery on the side of the portion 21a. From this, the configuration of the heat exchanger 1 can be realized using, for example, a conventional bending jig by changing the stopper jig 22.

  Further, in the method of manufacturing the heat exchanger 1, the flat heat exchanger 100 having the plurality of heat transfer tubes 2 and the plurality of fins 4 is arranged in the arrangement direction 31 of the heat transfer tubes 2 of the flat heat exchanger 100. And bending at the inclined bending position L1. From this, from the heat exchanger 100 in which the heat transfer pipe 2 and the fins 4 are joined as in the conventional heat exchanger, the bending position L1 is inclined and bending is performed, so that the heat having two surfaces different in the arrangement direction The exchanger 1 can be easily manufactured.

Second Embodiment
FIG. 5 is a block diagram of the outdoor unit of the air conditioning apparatus according to Embodiment 2 of the present invention. In the second embodiment, parts having the same configuration as in the first embodiment are assigned the same reference numerals and descriptions thereof will be omitted. The heat exchanger 101 shown in FIG. 5 is different in inclination direction from the heat exchanger 1 of FIG.

  When the heat exchanger 101 is installed on the horizontal bottom plate 6 of the housing 9, the second heat exchange unit 101 b is inclined forward to the inside of the housing 9 in the thickness direction of the heat exchanger 1. And as FIG. 5 shows, the 2nd heat exchange part 101b of the heat exchanger 101 is arrange | positioned closer to the back surface of the housing | casing 9 from upper side below. Therefore, the condensed water etc. which arose in the 2nd heat exchange part 101b of the heat exchanger 101 are drained along the sliding direction 111 shown by the arrow in FIG. Specifically, dew condensation water of the heat transfer pipe 2 slides the outer periphery of the heat transfer pipe 2 toward the inside of the outdoor unit 10, ie, the fan 3 side in FIG. It falls toward the bottom surface 9 a of the body 9 or travels downward along the fins 4. On the other hand, the first heat exchange portion 101a is inclined rearward in the thickness direction of the heat exchanger 101, and the upper side is disposed closer to the side surface of the housing 9 than the lower side. Therefore, dew condensation water or the like generated in the first heat exchange portion 101 a slides toward the side of the housing 9 and falls toward the bottom 9 a of the housing 9 at the rear end of the heat transfer tube 2 or Move down along the fin 4.

  The flow direction 32 of the air is shown by the arrow in FIG. During operation of the fan 3, air outside the outdoor unit 10 is sucked into the outdoor unit 10 from the back and side surfaces of the housing 9, and the sucked air passes through the gap between the heat transfer tube 2 and the fins 4. It is discharged to the outside of the outdoor unit 10 through. Further, as described above, the condensed water and the like of the second heat exchange unit 101b move along the sliding direction 111. Therefore, water such as dew condensation water is energized by the flow of air generated by driving the fan 3.

  In the heat exchanger 1 of FIG. 2, the bending position L1 is set to be inclined at an angle θ from the arrangement direction 31 of the heat transfer tubes 2 to the R1 direction. However, the heat exchanger 101 of FIG. It can be manufactured by performing bending processing while setting the angle θ inclined in the opposite direction.

  In addition, the heat exchanger 101 is arranged such that the positions and directions of the first stopper jig 22a and the second stopper jig 22b are vertically inverted on the bending jig 21 in the manufacturing apparatus 20 shown in FIGS. 4A to 4C. It can be manufactured by the device. In this case, the heat exchanger 101 is installed and bent in the bending jig 21 in a state in which the arrangement direction of the heat transfer tubes 2 is inclined at an angle θ from the movable shaft 21c of the movable portion 21a in the direction opposite to the R2 direction of FIG. Ru. Also in the second embodiment, as in the first embodiment, the shock absorbing material 5 may be provided between the heat exchanger 101 and the bottom plate 6. In this case, the cushioning material 5 may be disposed in the thickness direction of the heat exchanger 101 such that the inclination is opposite to that in the first embodiment.

  Also in the second embodiment, in the heat exchanger 101, the arrangement direction 131b of the heat transfer tubes 2 in the second heat exchange unit 101b is inclined to the arrangement direction 131a of the heat transfer tubes 2 in the first heat exchange unit 101a.

  Thus, in the heat exchanger 101 of the second embodiment, drainage is promoted as in the first embodiment, and frost formation can be suppressed. Specifically, accumulation of condensation water and the like from the upper heat transfer pipe 2 in the lower heat transfer pipe 2 is suppressed. Further, since the condensed water and the like generated in the heat exchanger 101 can be discharged quickly, the defrosting operation time can be shortened and the rising of the heating performance in the next operation can be improved.

  In the heat exchanger 1 of the outdoor unit 10, the first heat exchange unit 1 a faces the side of the case 9 and the second heat exchange unit 1 b faces the back of the case 9 in the case 9. The arrangement direction 131 b of the heat transfer tubes 2 in the second heat exchange unit 101 b is inclined toward the front side of the housing 9.

  Since air flows in the direction in which the condensed water etc. descends the heat transfer pipe 2 from this, the condensed water etc. can be scattered or the lubricating water can be energized and discharged from the heat exchanger 1 as needed. Moreover, the growth of frost can be suppressed by this, and heating continuous operation time can be kept long.

Third Embodiment
FIG. 6 is a partial configuration diagram of a heat exchanger according to Embodiment 3 of the present invention. In FIG. 6, the arrangement direction of the heat transfer tubes 2 is shown to be along the vertical direction in the drawing. Also in the third embodiment, in the heat exchanger 1, the arrangement direction 31b in the second heat exchange portion 1b is inclined to the arrangement direction 31a in the first heat exchange portion 1a, and the same effect as in the first embodiment have. The same components as those in the first embodiment will be assigned the same reference numerals and descriptions thereof will be omitted.

  In the third embodiment, the groove 40 a is formed in the fin 40. The groove 41a may be a groove formed by indenting the surface, or may be a through hole. The groove 41 a is formed along the joint between the fin 40 and the heat transfer tube 2. Specifically, the groove 41 a is provided along the end 2 b of the heat transfer tube 2 in the thickness direction of the heat exchanger 1.

  When the heat exchanger 1 is installed in the outdoor unit 10, the second heat exchange unit 1b disposed along the rear surface of the housing 9 is inclined backward, and condensation water and the like move in the sliding direction 11. In the groove 41a formed in the end 2b, drainage is promoted by capillary action. In particular, when the groove portion 41a is formed in the end portion 2b of the end portion 2a and the end portion 2b of the heat transfer tube 2 positioned below in the direction of gravity, the condensed water which has moved along the heat transfer tube 2 to the end portion 2b Etc. are efficiently guided downward.

  The groove portion 41 a may have any shape as long as it forms a water flow path for guiding condensed water from the heat transfer pipe 2 and discharging the condensed water. The fin 40 of the third embodiment can also be applied to the second embodiment. Although FIG. 6 illustrates the case where the groove 41a is formed at the position of the end 2b, it may be provided only at the position of the end 2a or at the positions of the end 2a and the end 2b. When the groove 41a is formed in the fin 4 of the heat exchanger 101 according to the second embodiment, the second heat exchange portion 101b is inclined forward, so the groove 41a is formed at the position of the end 2a on the front side. Thus, the same effects as those described above can be obtained. In the case where the heat exchanger 1 is installed in the outdoor unit 10, for example, the first heat exchange unit 1a is inclined to the housing 9 side and the second heat exchange unit 1b is inclined to the inside of the housing 9 In the first heat exchange section 1a and the second heat exchange section 1b, drainage is promoted by forming the grooves 41a at the positions of both the end 2a and the end 2b. Alternatively, the groove 41 a may be provided at an end of the first heat exchange unit 1 a and the second heat exchange unit 1 b that is positioned below the larger installation area.

  In the third embodiment, grooves 41 a are formed in the fins 40 at the positions of the end portions 2 a and 2 b of the heat transfer tube 2. From this, the groove 41a can move the condensed water etc. which has moved to the end 2b of the heat transfer tube 2 further from the end 2b by capillary action. Therefore, the groove portion 41a can promote drainage from the heat transfer tube 2 and suppress frost formation due to condensation water or the like staying in the end portion 2b.

  Further, the groove portion 41 a is formed at the end portion 2 b of the end portions 2 a and 2 b of the heat transfer tube 2 which is positioned below in the gravity direction. Since the heat exchanger 1 can further move the condensed water etc. which has moved to the end 2b of the heat transfer tube 2 from the end 2b by the groove 41a, the heat exchanger 1 can be moved away from the heat exchanger 1 It can drain efficiently.

Fourth Embodiment
The heat exchanger 1 of the fourth embodiment will be described based on FIG. Also in the fourth embodiment, in the heat exchanger 1, the arrangement direction 31b of the second heat exchange unit 1b is inclined to the arrangement direction 31a of the first heat exchange unit 1a. In the fourth embodiment, the same components as those of the third embodiment are designated by the same reference numerals and the description thereof will be omitted.

  The fourth embodiment will be described focusing on the region where the groove 41a is provided. The groove portion 41 a formed in the fin 40 is provided in an arc shape along the end portion 2 b of the heat transfer tube 2. In the groove 41a, drainage is promoted by capillary action. Further, when the groove 41a is formed corresponding to the end 2b positioned downward in the direction of gravity, the groove 41a efficiently guides the dew condensation water etc. which has moved along the heat transfer tube 2 to the end 2b. be able to. In particular, when the groove 41a is formed corresponding to the upper portion of the end 2b, the groove 41a is a position away from the end 2b of the heat transfer tube 2 in the lower direction in the front-rear direction (arrow X direction) of the outdoor unit 10. Can lead condensation water downward.

  In the fourth embodiment, the groove portion 41 a is formed in an arc shape along the end portion 2 b of the heat transfer tube 2. From this, the groove 41a can move the condensed water etc. which has moved to the end 2b of the heat transfer tube 2 further from the end 2b by capillary action. Therefore, the groove 41 b can promote drainage from the heat transfer tube 2 and prevent condensation water and the like from staying in the end 2 b. In particular, since the groove 41 b is provided in an arc shape, it is possible to guide condensation water and the like downward by its curved surface.

Embodiment 5
FIG. 7 is a partial configuration diagram of a heat exchanger according to Embodiment 5 of the present invention. Also in the fifth embodiment, in the heat exchanger 1, the arrangement direction 31b of the second heat exchange unit 1b is inclined to the arrangement direction 31a of the first heat exchange unit 1a. In the fifth embodiment, the same components as those of the third embodiment are designated by the same reference numerals and the description thereof will be omitted.

  The fifth embodiment will be described focusing on the region where the groove 41b is provided. The grooves 41 b are provided linearly in the arrangement direction of the plurality of heat transfer tubes 2. With such a groove 41 b structure, the heat exchanger 1 can promote drainage regardless of the shape of the heat transfer tube 2. In particular, as shown in FIG. 7, when the groove 41b is continuously formed at the end of the plurality of heat transfer tubes 2, the condensed water moved along the groove 41b from the upper heat transfer tube 2 is By combining with the condensed water from the heat transfer tube 2, the droplets become large and are easily drained by gravity.

  In addition, although the structure which processes the groove part 41b into linear form was demonstrated based on FIG. 7, it is not specifically limited to this. The grooves 41 b may be provided intermittently in the arrangement direction of the heat transfer tubes 2.

  In the fifth embodiment, the groove portion 41 b is formed in a straight line in the arrangement direction of the plurality of heat transfer tubes 2. From this, the groove 41b moves condensed water and the like from the heat transfer pipe 2 by capillary phenomenon, and combines the condensed water and the like moved from the plurality of heat transfer pipes 2 to increase the mass of water droplets, thereby draining by gravity. It can be made easy.

Sixth Embodiment
FIG. 8 is a partial configuration diagram of a heat exchanger according to Embodiment 6 of the present invention. Also in the sixth embodiment, in the heat exchanger 1, the arrangement direction 31b of the second heat exchange unit 1b is inclined to the arrangement direction 31a of the first heat exchange unit 1a. In the sixth embodiment, the same components as those of the third embodiment are designated by the same reference numerals and the description thereof will be omitted.

  The sixth embodiment will be described focusing on the area where the groove 41c is provided. The groove portion 41 c is provided in an inclined linear shape at the end portion 2 b of the heat transfer tube 2. In the groove 41c, drainage is promoted by capillary action. Further, when the groove 41c is formed corresponding to the end 2b located downward in the direction of gravity, the groove 41c efficiently guides the dew condensation water and the like moving along the heat transfer tube 2 to the end 2b downward. be able to. Particularly, as shown in FIG. 8, when the groove 41c is provided on the upper side of the end 2b, the dew condensation water or the like moved to the end 2b of the heat transfer tube 2 is inclined downward. It is guided downward by

  In the sixth embodiment, the groove 41 c is formed in an inclined linear shape at the end 2 b of the heat transfer tube 2. Thus, the groove 41c can move the condensed water and the like moved to the end 2b of the heat transfer tube 2 from the end 2b by capillary action. Therefore, the groove 41c can promote drainage from the heat transfer tube 2 and prevent condensation water and the like from staying in the end 2b. In particular, since the groove 41c is provided in an inclined linear shape, dew condensation water and the like can be guided downward by the inclination.

Embodiment 7
FIG. 9 is a partial configuration diagram of a heat exchanger according to Embodiment 7 of the present invention. Also in the seventh embodiment, in the heat exchanger 1, the arrangement direction 31b of the second heat exchange unit 1b is inclined to the arrangement direction 31a of the first heat exchange unit 1a. In the seventh embodiment, the same components as those of the third embodiment are designated by the same reference numerals and the description thereof will be omitted.

  The seventh embodiment will be described focusing on the region where the groove 41 d is provided. The groove 41 d is provided in an L shape along the end 2 b of the heat transfer tube 2. In the groove 41 d, drainage is promoted by capillary action. Further, when the groove 41d is formed corresponding to the end 2b located downward in the direction of gravity, the groove 41d efficiently leads downward the condensation water etc. which has moved along the heat transfer tube 2 to the end 2b. be able to. In particular, as shown in FIG. 9, when the groove 41d has a corner bent at a right angle to the upper portion of the end 2b, the drainage can be improved and drainage can be further promoted.

  The number of times the groove 41 d is bent is not limited to one, and may be two or more. Further, in FIG. 9, one side of the L-shaped groove portion 41d is provided in the direction perpendicular to the arrangement direction of the heat transfer tubes 2, but it is not particularly limited thereto.

  In the seventh embodiment, the groove 41 d is formed in an L shape at the end 2 b of the heat transfer tube 2. Thus, the groove 41 d can move the condensed water and the like moved to the end 2 b of the heat transfer tube 2 further from the end 2 b by capillary action. Therefore, the groove 41 d can promote drainage from the heat transfer tube 2 and prevent condensation water and the like from staying in the end 2 b. In particular, the groove 41 d is provided in an L-shape having a corner, so that water drainage can be improved.

Eighth Embodiment
FIG. 10 is a partial configuration diagram of a heat exchanger according to Embodiment 8 of the present invention. Also in the eighth embodiment, in the heat exchanger 1, the arrangement direction 31b of the second heat exchange unit 1b is inclined to the arrangement direction 31a of the first heat exchange unit 1a. In the sixth embodiment, the same components as those of the third embodiment are designated by the same reference numerals and the description thereof will be omitted.

  The eighth embodiment will be described focusing on the region where the groove 41e is provided. The groove 41 e is provided along the end 2 b of the heat transfer tube 2 by being bent at an obtuse angle. In the groove 41e, drainage is promoted by capillary action. Further, when the groove 41e is formed corresponding to the end 2b located downward in the direction of gravity, the groove 41e efficiently guides the dew condensation water etc. which has moved along the heat transfer tube 2 to the end 2b. be able to. In particular, the groove 41 e shown in FIG. 10 has a corner bent as in the groove 41 d of the seventh embodiment, so that the water drainage can be improved. Further, the groove 41e can set the angle of bending in a direction in which drainage can be easily performed with respect to the inclination angle of the first heat exchange unit 1a or the second heat exchange unit 1b, and the drainage can be further improved. For example, when the bending angle of the groove 41e is formed to be larger than the right angle by the angle θ, one side of the groove 41e can be configured to be in the vertical direction in a state where the heat exchanger 1 is installed.

  Although FIG. 10 shows the case where the number of turns is one in the groove 41e, the number of turns may be two or more. The other side of the groove 41 e may not be perpendicular to the arrangement direction of the heat transfer tubes 2.

  In the eighth embodiment, the groove 41 e is formed in an L shape along the end 2 b of the heat transfer tube 2. Thereby, the condensed water etc. which have moved to the end 2b of the heat transfer tube 2 can be further moved from the end 2b by capillary action. Therefore, the groove 41 e can promote drainage from the heat transfer tube 2 and prevent condensation water and the like from staying in the end 2 b. In particular, when the groove 41e is provided in an L-shape bent at an obtuse angle, water drainage can be improved and the drainage angle can be further improved by setting the bending angle according to the inclination angle θ of the heat exchanger 1 it can.

  The embodiment of the present invention is not limited to the above embodiment, and various modifications can be made. For example, in addition to the plurality of fins 4 and the plurality of heat transfer tubes 2, the bending process includes an inflow side distributor that allows the working fluid to flow into the heat transfer pipe 2, and an outflow side distributor that causes the working fluid to flow out of the heat transfer pipe 2. May be implemented for an integrated heat exchanger.

  Further, the shape of the heat exchangers 1 and 101 is not limited to the L-shaped one. The heat exchangers 1 and 101 are, for example, U-shaped having three heat exchange parts, and three heat exchange parts are disposed opposite to each other on both sides and the back of the outdoor unit 10, respectively. It may be. The U-shaped heat exchanger can, for example, be symmetrical with respect to the central second heat exchanger. And in the state installed in outdoor unit 10, the 2nd heat exchange part by the side of the back of a U-shaped heat exchanger for example inclines backwards, and the two 1st heat exchange parts by the side of a side incline forward, respectively.

  Moreover, although the case where the 1st heat exchange part 1a and the 2nd heat exchange part 1b were integral was demonstrated, you may be comprised as another body.

  1, 100, 101 heat exchanger, 1a, 101a first heat exchange unit, 1b, 101b second heat exchange unit, 1c corner, 1e, 100e bottom, 100d side, 2 heat transfer tubes, 2a, 2b end, 3 Fan, 4, 40 fins, 41a to 41e grooves, 5 cushioning materials, 5a inclined surface, 6 bottom plate, 9 case, 9a case bottom surface, 10 outdoor unit, 11, 111 sliding direction, 20 manufacturing device, 21 bending jig , 21a movable portion, 21b fixed portion, 21c movable shaft, 22 stopper jig, 22a first stopper jig, 22b second stopper jig, 23 bending die, 23a straight portion, 23b guide portion, 24 bending direction 31, 31a, 31b , 131a, 131b (in heat transfer tube) arrangement direction, 32 air flow direction, L0, L1 bending position, R1, R2 direction, θ angle.

Claims (18)

A first heat exchange portion having a plurality of heat transfer tubes arranged in one direction through which a working fluid flows, and a plurality of fins connected to the plurality of heat transfer tubes and arranged in the other direction;
A plurality of heat transfer tubes and a plurality of fins, and the first heat exchange unit includes a second heat exchange unit bent so that the arrangement direction of the fins is different from the first heat exchange unit;
An arrangement direction of the heat transfer tubes in the second heat exchange unit is inclined to an arrangement direction of the heat transfer tubes in the first heat exchange unit. The first heat exchange portion and the second heat exchange portion are integrally configured, and a corner portion which is a boundary portion between the first heat exchange portion and the second heat exchange portion is constant from the bottom to the top The heat exchanger according to claim 1, having a curvature.   The heat exchanger according to claim 1, wherein the heat transfer tube is a flat tube.   The heat exchanger according to any one of claims 1 to 3, wherein a groove is formed in the fin at a position of an end of the heat transfer tube.   The heat exchanger according to claim 4, wherein the groove portion is formed in an arc shape along the end portion of the heat transfer pipe.   The heat exchanger according to claim 4, wherein the groove portion is formed in an inclined linear shape at the end of the heat transfer pipe.   The heat exchanger according to claim 4, wherein the groove portion is formed in an L shape at the end of the heat transfer tube.   The heat exchanger according to claim 4, wherein the groove portion is formed in a linear shape in the arrangement direction of the heat transfer tubes.   The heat exchanger according to any one of claims 4 to 8, wherein the groove portion is formed at an end portion of the end portion of the heat transfer pipe, which is located downward in a gravity direction.   The shock absorbing material according to any one of claims 1 to 9, further comprising: a shock absorbing material provided at a bottom portion of the first heat exchange portion and having an inclined surface corresponding to an inclination of the heat transfer tubes in the first heat exchange portion. Heat exchanger.   The shock absorbing material according to any one of claims 1 to 10, further comprising: a shock absorbing material provided at the bottom of the second heat exchange unit, and having an inclined surface corresponding to the inclination direction of the heat transfer tubes in the second heat exchange unit. Heat exchanger.   The heat exchanger according to claim 10, wherein the buffer material is composed of an insulating material that electrically insulates. And
An outdoor unit comprising: the heat exchanger according to any one of claims 1 to 12 installed in the housing. The heat exchanger is installed in the housing such that the first heat exchange portion faces the side surface of the housing, and the second heat exchange portion faces the rear surface of the housing.
The outdoor unit according to claim 13, wherein an arrangement direction of the heat transfer tubes in the second heat exchange unit is inclined to a back side of the housing. The heat exchanger is installed in the housing such that the first heat exchange portion faces the side surface of the housing, and the second heat exchange portion faces the rear surface of the housing.
The outdoor unit according to claim 13, wherein an arrangement direction of the heat transfer tubes in the second heat exchange portion is inclined to a front side of the housing.   The outdoor unit according to any one of claims 13 to 15, wherein the working fluid is an HFC refrigerant, an HFO refrigerant, or a mixed refrigerant of an HFC refrigerant and an HFO refrigerant. An apparatus for manufacturing a heat exchanger according to any one of claims 1 to 12,
A plurality of heat transfer tubes and a plurality of the fins, which have a fixed portion and a movable portion disposed with a gap between the fixed portion and rotating toward the fixed portion about a movable axis; A bending jig on which a flat plate-like heat exchanger is installed;
A stop jig provided in the bending jig and supporting the flat heat exchanger installed in the bending jig such that the arrangement direction of the heat transfer tubes is inclined with respect to the movable axis;
And a bending die disposed at a position facing the bending jig with the heat exchanger interposed therebetween and having a curved outer periphery along the gap on the movable portion side. A method of manufacturing a heat exchanger according to any one of claims 1 to 12,
Bending a flat heat exchanger having a plurality of heat transfer tubes and a plurality of fins at a bending position inclined to the arrangement direction of the heat transfer tubes of the flat heat exchanger How to make an exchange.

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