Abstract:
Provided is a heat exchanger, which includes a plurality of tubes and a plurality of fins. The tubes accommodate respective refrigerant passages through which refrigerant flows. The fins having a plate shape are spaced apart from each other, and include a plurality of through holes through which the tubes pass, respectively. The fin is provided with a condensate water guide part guiding discharge of condensate water generated during heat exchange between air and the refrigerant flowing through the tube. Accordingly, adhesion of the tube and the fin is facilitated, the distance between neighboring fins is maintained, and condensate water is efficiently discharged.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     The present application claims the benefit of priority under 35 U.S.C. 119 to Korean Patent Application No. 10-2011-0037412 (filed on Apr. 21, 2011) which is hereby incorporated by reference in its entirety. 
     BACKGROUND 
     The present disclosure relates to a heat exchanger. 
     Heat exchangers exchange heat between refrigerant flowing therein and indoor or outdoor air. Such a heat exchanger includes a tube and a plurality of fins for increasing a heat exchange area between air and refrigerant flowing through the tube. 
     Heat exchangers are classified into fin-and-tube type ones and micro-channel type ones, according to their shapes. A fin-and-tube type heat exchanger includes a plurality of fins and a tube passing through the fins. A micro-channel type heat exchanger a plurality of flat tubes and a fin bent at several times within between the flat tubes. Both the fin-and-tube type heat exchanger and the micro-channel type heat exchanger exchange heat between an outer fluid and refrigerant flowing within the tube or the flat tube, and the fins increase a heat exchange area between the outer fluid and the refrigerant flowing within the tube or the flat tube. 
     However, such heat exchangers have the following limitations. 
     First, the tube of a fin-and-tube type heat exchanger passes through the fins. Thus, even when condensate water generated while the fin-and-tube type heat exchanger operates as an evaporator flows down along the fins, or is frozen onto the outer surface of the tube or the fins, the heat exchanger can efficiently remove the condensate water. However, since fin-and-tube type heat exchangers include only a single refrigerant passage in the tube, heat exchange efficiency of the refrigerant is substantially low. 
     On the contrary, since a micro-channel type heat exchanger includes a plurality of refrigerant passages within the flat tube, the micro-channel type heat exchanger is higher in heat exchange efficiency of the refrigerant than a fin-and-tube type heat exchanger. However, micro-channel type heat exchangers include the fin between the flat tubes. Thus, condensate water generated while a micro-channel type heat exchanger operates as an evaporator may be substantially frozen between the flat tubes. In addition, the frozen water may substantially degrade the heat exchange efficiency of the refrigerant. 
     SUMMARY 
     Embodiments provide a heat exchanger having high heat exchange efficiency. 
     Embodiments also provide a heat exchanger for more simply improve heat exchange efficiency. 
     In one embodiment, a heat exchanger includes: a plurality of tubes accommodating respective refrigerant passages through which refrigerant flows; and a plurality of fins having a plate shape, spaced apart from each other, and including: a plurality of through holes through which the tubes pass, respectively, wherein the fin is provided with a condensate water guide part guiding discharge of condensate water generated during heat exchange between air and the refrigerant flowing through the tube. 
     In another embodiment, a heat exchanger includes: a plurality of tubes accommodating respective refrigerant passages through which refrigerant flows; and a plurality of fins having a plate shape, spaced apart from each other, and including a plurality of through holes through which the tubes pass, respectively, each of the fins including a first slope, a second slope, and a plurality of louvers, wherein the first slope is provided in two, which are inclined upward in a width direction of the fin from a surface of the fin, at both side ends of the fin; the second slope is provided in two, which are inclined downward in the width direction of the fin, at respective ends of the first slopes, and having respective ends connected to each other; and the louvers are provided on the second slopes. 
     The details of one or more embodiments are set forth in the accompanying drawings and the description below. Other features will be apparent from the description and drawings, and from the claims. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a front view illustrating a heat exchanger according to a first embodiment. 
         FIG. 2  is a cross-sectional view illustrating a principal part of the heat exchanger of  FIG. 1 . 
         FIG. 3  is a cross-sectional view illustrating a principal part of a heat exchanger according to a second embodiment. 
         FIG. 4  is a front view illustrating a principal part of a fin constituting a heat exchanger according to a third embodiment. 
         FIG. 5  is a cross-sectional view illustrating a fin according to the third embodiment. 
         FIG. 6  is a front view illustrating a principal part of a fin constituting a heat exchanger according to a fourth embodiment. 
         FIG. 7  is a cross-sectional view illustrating a fin according to the fourth embodiment. 
         FIG. 8  is a graph illustrating fan power and heat transfer capacity of a heat exchanger according to fin shapes in accordance with the third and fourth embodiments. 
         FIG. 9  is a front view illustrating a principal part of a fin constituting a heat exchanger according to a fifth embodiment. 
         FIG. 10  is a cross-sectional view illustrating a fin according to the fifth embodiment. 
         FIG. 11  is a front view illustrating a principal part of a fin constituting a heat exchanger according to a sixth embodiment. 
         FIG. 12  is a cross-sectional view illustrating a fin according to the sixth embodiment. 
         FIG. 13  is a front view illustrating a principal part of a fin constituting a heat exchanger according to a seventh embodiment. 
         FIG. 14  is a cross-sectional view illustrating a fin according to the seventh embodiment. 
         FIG. 15  is a graph illustrating fan power and heat transfer capacity of a heat exchanger according to the presence and position of louvers in accordance with the seventh embodiment. 
         FIG. 16  is a front view illustrating a principal part of a fin constituting a heat exchanger according to an eighth embodiment. 
         FIG. 17  is a cross-sectional view illustrating a fin according to the eighth embodiment. 
         FIG. 18  is a front view illustrating a principal part of a fin constituting a heat exchanger according to a ninth embodiment. 
         FIG. 19  is a cross-sectional view illustrating a fin according to the ninth embodiment. 
         FIG. 20  is a front view illustrating a principal part of a fin constituting a heat exchanger according to a tenth embodiment. 
         FIG. 21  is a cross-sectional view illustrating a fin according to the tenth embodiment. 
     
    
    
     DETAILED DESCRIPTION OF THE EMBODIMENTS 
     Reference will now be made in detail to the embodiments of the present disclosure, examples of which are illustrated in the accompanying drawings. 
       FIG. 1  is a front view illustrating a heat exchanger according to a first embodiment.  FIG. 2  is a cross-sectional view illustrating a principal part of the heat exchanger of  FIG. 1 . 
     Referring to  FIGS. 1 and 2 , a heat exchanger  100  according to the current embodiment includes: a plurality of fins  110  having a plate shape; a plurality of tubes  120  passing through the fins  110 ; and a plurality of headers  130  disposed at both sides of the tubes  120  to connect corresponding ends of the tubes  120  to one another. That is, the fins  110  are not disposed between the tubes  120 , and the tubes  120  pass through the fins  110 . 
     In more detail, the fins  110  have a rectangular plate shape with a predetermined length. The fins  110  substantially increase a heat exchange area between an external fluid and refrigerant flowing through the tubes  120 . The fins  110  are spaced a predetermined distance from one another such that each of both side surfaces of the fins  110  faces a side surface of a neighboring one of the fins  110 . 
     To this end, each of the fins  110  has through holes  111 . The tubes  120  pass through the through holes  111 . The through holes  111  are spaced apart from one another in the longitudinal direction of the fins  110  by a predetermined distance, substantially by a distance between the tubes  120 . 
     Each of the fins  110  is provided with ribs  113 . The ribs  113  are disposed at a side of the fins  110  to correspond to the periphery of the through holes  111 . Thus, substantially, the ribs  113  may have a tube shaped inner surface corresponding to the outer surface of the tubes  120 . 
     In more detail, the ribs  113  are perpendicular to a surface of the fins  110 . The ribs  113  tightly contact the outer surface of the tubes  120  passing through the fins  110 . That is, the ribs  113  may substantially increase an adhering area between the fin  110  and the tube  120 . 
     The ribs  113  have a length corresponding to a distance between neighboring ones of the fins  110 . When the tube  120  passes through the fins  110 , the front end of the rib  113  provided to one of neighboring ones of the fins  110  contacts a surface of the other one. Thus, the rib  113  substantially maintains the distance between the neighboring fins  110 . 
     For example, the tubes  120  may be longitudinally elongated through extrusion molding. The tubes  120  pass through the fins  110  such that the tubes  120  are spaced a predetermined distance from one another in the longitudinal direction of the fins  110 . The tubes  120  may be hollow bodies having a predetermined length along a straight line. Refrigerant passages (not shown) through which the refrigerant flows are disposed within the tubes  120 . 
     The fins  110  are coupled and fixed to the tubes  120  through brazing. Referring to  FIG. 2 , a sheet-shaped brazing material  140  is placed on the outer surfaces of the tubes  120 , and then, the fins  110  are coupled to the tubes  120 . At this point, the brazing material  140  is substantially disposed between the outer surface of the tubes  120  and the inner surface of the ribs  113 . Then, the fins  110 , the tubes  120 , and the brazing material  140  are heated to a predetermined temperature. Accordingly, the brazing material  140  is melted to fix the fins  110  and the tubes  120 . 
     The headers  130  are connected to both the ends of the tubes  120 , respectively. The headers  130  distribute the refrigerant to the tubes  120 . To this end, baffles (not shown) are disposed within the headers  130 . 
     Hereinafter, a method of manufacturing a heat exchanger will now be described according to the first embodiment. 
     First, the tubes  120  are coupled to the fins  110  provided in a stacked structure. The tubes  120  with the brazing material  140  on the outer surfaces thereof sequentially pass through the through holes  111  of the fins  110 . Thus, when the tubes  120  pass through the fins  110 , the outer surfaces of the tubes  120  substantially approach the inner surfaces of the ribs  113 . 
     When the fins  110  are stacked, the front end of the ribs  113  of the fins  110  tightly contacts a surface of adjacent ones of the fins  110 . Thus, neighboring ones of the fins  110  are spaced apart from each other by the distance corresponding to the length of the ribs  113 . 
     The brazing material  140  is disposed between each of the tubes  120  and the fins  110 . For example, when the brazing material  140  is attached in the form of sheet to the outer surfaces of the tubes  120 , the fins  110  may be coupled to the tubes  120 . Thus, the brazing material  140  may be substantially disposed between the outer surface of the tubes  120  and the inner surface of the ribs  113 . 
     Next, the fins  110  and the tubes  120  are fixed through brazing. For example, when the fins  110  and the tubes  120  are heated to a predetermined temperature, for example, to a temperature ranging from about 500° C. to about 700° C., the brazing material  140  are melted to fix the fins  110  and the tubes  120 . 
     Meanwhile, as described above, the brazing material  140  is disposed between the outer surface of the tubes  120  and the inner surface of the ribs  113 . Thus, the area of the inner surface of the ribs  113  is substantially equal to the adhering area between the tube  120  and the fin  110 . That is, the ribs  113  increase the adhering area between the tube  120  and the fin  110 , thereby increasing adhering strength between the tube  120  and the fin  110 . In addition, the ribs  113  substantially maintain the distance between the neighboring fins  110 . 
     Hereinafter, a heat exchanger according to a second embodiment will now be described with reference to the accompanying drawing. 
       FIG. 3  is a cross-sectional view illustrating a principal part of a heat exchanger according to the second embodiment. Like reference numerals denote like elements in the first and second embodiments, and a description of the same components as those of the first embodiment will be omitted in the second embodiment. 
     Referring to  FIG. 3 , first fins  210  and second fins  220  are provided according to the current embodiment. The first and second fins  210  and  220  are provided with through holes  211  through which tubes  120  pass. First and second ribs  213  and  215  are provided only to the first fins  210 . That is, the second fins  220  have a plate shape, like fins applied to a related art heat exchanger. 
     The first and second ribs  213  and  215  extend in different directions. That is, the first ribs  213  extend to the left side of  FIG. 3  from the left surfaces of the first fins  210 , and the second ribs  215  extend to the right side of  FIG. 3  from the right surfaces of the first fins  210 . A plurality of the first ribs  213  and a plurality of second ribs  215  are alternately disposed at the peripheries of the through holes  211  that are vertically spaced apart from one another in the first fins  210 . That is, when the first rib  213  is disposed at the periphery of the through hole  211  disposed at the upper end of the first fins  210 , the second rib  215  is disposed at the periphery of the through hole  211  disposed under the first rib  213 . In a same manner, a plurality of the first fins  210  and a plurality of the second fins  220  are alternately disposed in the longitudinal direction of the tubes  120 . In this case, the second fins  220  may be disposed in positions closest to headers  230 . 
     Hereinafter, a heat exchanger according to third and fourth embodiments will now be described with reference to the accompanying drawings. 
       FIG. 4  is a front view illustrating a principal part of a fin constituting a heat exchanger according to the third embodiment.  FIG. 5  is a cross-sectional view illustrating a fin according to the third embodiment.  FIG. 6  is a front view illustrating a principal part of a fin constituting a heat exchanger according to the fourth embodiment.  FIG. 7  is a cross-sectional view illustrating a fin according to the fourth embodiment.  FIG. 8  is a graph illustrating fan power and heat transfer capacity of a heat exchanger according to fin shapes in accordance with the third and fourth embodiments. 
     Referring to  FIGS. 4 and 5 , an outer surface of a fin  310  according to the third embodiment is provided with a condensate water discharge part  313  for discharging condensate water. The condensate water discharge part  313  is formed substantially by recessing and projecting a portion of the fin  310  corresponding to a space between neighboring through holes  311 . In more detail, the condensate water discharge part  313  includes a first guide part  314  and a second guide part  315 . The first guide part  314  and the second guide part  315  are formed substantially as a single body. 
     The first guide part  314  is inclined upward to the outside of the through hole  311  from a portion of the fin  310  adjacent to the periphery of the through hole  311 . The outer edge of the first guide part  314  is connected to the second guide part  315 . 
     The second guide part  315  includes two first slopes  316  and two second slopes  317 . The first slopes  316  extend in the width direction of the fin  310 , at the lateral ends of the fin  310 . Each of the second slopes  317  extends in the width direction of the fin  310 , at the end of the first slope  316  corresponding to the space between the through holes  311 . 
     The first slopes  316  are inclined upward from a surface of the fin  310  at the lateral ends of the fin  310 . Each of the second slopes  317  is inclined downward from a surface of the fin  310 , at an end of the first slope  316 . Thus, substantially, a portion where ends of the first slopes  316  meet ends of the second slopes  317  constitutes a ridge, and a portion where ends of the second slopes  317  are connected to each other constitutes a valley, thereby forming an uneven structure. 
     An end of the first slopes  316  is connected to an end of the second slopes  317  in a region between one of both side ends of the fin  310  and one of imaginary lines (hereinafter, referred to as first lines X) passing through both the side ends of the through holes  311  in the longitudinal direction of the fin  310 . Ends of the second slopes  317  are connected to each other on an imaginary line (hereinafter, referred to as a second line Y) passing through the center of the width of the through holes  311  in the longitudinal direction of the fin  310 . The second slopes  317  are substantially longer than the first slopes  316  in the width direction of the fin  310 . 
     Accordingly, condensate water, which is generated at a side of the tube  120  and the fin  310  adjacent to the tube  120  while a heat exchanger  300  is operated, is substantially guided along the first guide part  314  and the second guide part  315 . The condensate water substantially flows downward along both the side ends of the fin  310 , that is, along the first slopes  316 . Thus, condensate water is efficiently discharged from a surface of the fin  310  to prevent freezing, thereby substantially improving heat exchange efficiency of the heat exchanger  300 . 
     Referring to  FIGS. 6 and 7 , according to the fourth embodiment, first and second slopes  416  and  417  constituting a second guide part  415  have the same length in the width direction of a fin  410  To this end, ends of the first and second slopes  416  and  417  are connected to each other in the region between the first line X and the second line Y. Thus, substantially, the length of the first slopes  416  in the width direction of the fin  410  is further increased, and the length of the second slopes  417  is further decreased than those of the first embodiment. 
     Referring to  FIG. 8 , effects according to the third and fourth embodiments can be predicted. In detail, an X axis and a Y axis of  FIG. 8  denote fan power (W) and heat transfer capacity (kW) of a heat exchanger, respectively. Line A of  FIG. 8  corresponds to a heat exchanger including a fin in which an end of a first slope is connected to an end of a second slope on the first line X. Line B and line C of  FIG. 8  correspond to heat exchangers including fins according to the third and fourth embodiments, respectively. In these cases, the other conditions except for the shapes of the fins, that is, the conditions of tubes and fans are the same. As illustrated in  FIG. 8 , when fan power is fixed, the heat exchangers according to the third and fourth embodiments is higher in heat transfer efficiency than the heat exchanger including the fin in which the ends of the first and second slopes are connected on the first line X. Moreover, the heat exchanger according to the third embodiment is higher in heat transfer efficiency than the heat exchanger according to the fourth embodiment at the same fan power. 
     Hereinafter, a heat exchanger according to fifth and sixth embodiments will now be described with reference to the accompanying drawings. 
       FIG. 9  is a front view illustrating a principal part of a fin constituting a heat exchanger according to the fifth embodiment.  FIG. 10  is a cross-sectional view illustrating a fin according to the fifth embodiment.  FIG. 11  is a front view illustrating a principal part of a fin constituting a heat exchanger according to the sixth embodiment.  FIG. 12  is a cross-sectional view illustrating a fin according to the sixth embodiment. Like reference numerals denote like elements in the third to sixth embodiments, and a description of the same components as those of the third and fourth embodiments will be omitted in the fifth and sixth embodiments. 
     Referring to  FIGS. 9 and 10 , a second guide part  515  according to the fifth embodiment includes first to fourth slopes  516 ,  517 ,  518 , and  519 . The first slopes  516  are inclined upward in the width direction of the fin  510  at the lateral ends of a fin  510 . Each of the second slopes  517  is inclined downward in the width direction of the fin  510 , at an end of the first slope  516 . Each of the third slopes  518  is inclined upward in the width direction of the fin  510 , at an end of the second slope  517 . Each of the fourth slopes  519  is inclined downward in the width direction of the fin  510 , at an end of the third slope  518 . 
     Ends of the first and second slopes  516  and  517  are connected to each other between the first line X and one of both side ends of the fin  510 . Ends of the second and third slopes  517  and  518  are connected to each other between the first line X and the second line Y. Also, ends of the third and fourth slopes  518  and  519  are connected to each other between the first line X and the second line Y. In this case, the ends of the second and third slopes  517  and  518  are closer to the first line X, and the ends of the third and fourth slopes  518  and  519  are closer to the second line Y. Ends of the fourth slopes  519  are connected to each other on the second light Y. The second slopes  517  are longer than the first slopes  516  in the width direction of the fin  510 . The fourth slopes  519  are longer than the third slopes  518  in the width direction of the fin  510 . 
     Referring to  FIGS. 11 and 12 , the sixth embodiment is the same as the fifth embodiment in that a second guide part  615  according to the sixth embodiment includes first to fourth slopes  616 ,  617 ,  618 , and  619  that are inclined upward or downward in turn. However, the first to fourth slopes  616 ,  617 ,  618 , and  619  have the same length in the width direction of a fin  610 . 
     In addition, according to the length of the first and second slopes  616  and  617  in the width direction of the fin  610 , relative positions of a connected portion of the first and second slopes  616  and  617 , a connected portion of the second and third slopes  617  and  618 , and a connected portion of the third and fourth slopes  618  and  619 , to the first and second lines X and Y are different from that of the fifth embodiment. In more detail, ends of the first and second slopes  616  and  617  are connected to each other between the first line X and one of both side ends of the fin  610 . Ends of the second and third slopes  617  and  618  are connected to each other between the first line X and the second line Y. Also, ends of the third and fourth slopes  618  and  619  are connected to each other between the first line X and the second line Y. In this case, the ends of the second and third slopes  617  and  618  are closer to the first line X, and the ends of the third and fourth slopes  618  and  619  are closer to the second line Y. Ends of the fourth slopes  619  are connected to each other on the second light Y. 
     Hereinafter, a heat exchanger according to a seventh embodiment will now be described with reference to the accompanying drawings. 
       FIG. 13  is a front view illustrating a principal part of a fin constituting a heat exchanger according to the seventh embodiment.  FIG. 14  is a cross-sectional view illustrating a fin according to the seventh embodiment.  FIG. 15  is a graph illustrating fan power and heat transfer capacity of a heat exchanger according to the presence and position of louvers in accordance with the seventh embodiment. 
     Referring to  FIGS. 13 and 14 , a fin  710  according to the current embodiment is provided with a through hole  711  through which a tube (not shown) passes, and a condensate water discharge part  713  for discharging condensate water. The condensate water discharge part  713  includes a first guide part  714  and a second guide part  715 . The second guide part  715  includes two first slopes  716  and two second slopes  717 . 
     The above configuration of the fin  710 , that is, the through hole  711  and the condensate water discharge part  713  are the same as those of the third embodiment. Particularly, the seventh embodiment is the same as the third embodiment in that: the condensate water discharge part  713  includes the first guide part  714  and the second guide part  715 ; and the second guide part  715  includes the first slopes  716  and the second slopes  717 . 
     The fin  710  is provided with a plurality of louvers  720 . The louvers  720  may be formed by cutting portions of the fin  710 , substantially, by cutting portions of the condensate water discharge part  713  in the width direction of the fin  710 , and then, by bending the cut portions from the rest of the fin  710 . In the current embodiment, the louvers  720  are disposed only on the second slopes  717 . 
     Referring to  FIG. 15 , effects according to the seventh embodiment can be predicted. In more detail, an X axis and a Y axis of  FIG. 15  denote fan power (W) and heat transfer capacity (kW) of a heat exchanger, respectively. Line B of  FIG. 15  corresponds to a heat exchanger including the fin  310  according to the third embodiment, that is, a heat exchanger including a fin without a louver. Line B 1  of  FIG. 15  corresponds to a heat exchanger including the fin  710  according to the seventh embodiment, that is, a heat exchanger including the fin  710  having the louvers  720  only on the second slopes  717 . Line B 2  of  FIG. 15  corresponds to a heat exchanger including louvers disposed entirely on the second guide part  315  of the fin  310 , that is, a heat exchanger including the fin  310  having louvers on both the first and second slopes  316  and  317 . As illustrated in  FIG. 15 , when fan power is fixed, the heat exchanger according to the seventh embodiment is higher in heat transfer efficiency than the heat exchanger according to the third embodiment. However, the heat exchanger including louvers disposed on both the first and second slopes  316  and  317  is lower in heat transfer efficiency than the heat exchanger including the fin without a louver according to the third embodiment. This is because an increase of pressure loss due to louvers is greater than an increase of heat transfer efficiency due to the louvers. As a result, the heat transfer efficiency of the heat exchanger including louvers disposed on both the first and second slopes  316  and  317  is substantially decreased at the same fan output. 
     Hereinafter, a heat exchanger according to eighth to tenth embodiments will now be described with reference to the accompanying drawings. 
       FIG. 16  is a front view illustrating a principal part of a fin constituting a heat exchanger according to the eighth embodiment.  FIG. 17  is a cross-sectional view illustrating a fin according to the eighth embodiment.  FIG. 18  is a front view illustrating a principal part of a fin constituting a heat exchanger according to the ninth embodiment.  FIG. 19  is a cross-sectional view illustrating a fin according to the ninth embodiment.  FIG. 20  is a front view illustrating a principal part of a fin constituting a heat exchanger according to the tenth embodiment.  FIG. 21  is a cross-sectional view illustrating a fin according to the tenth embodiment. 
     Referring to  FIGS. 16 and 17 , a fin  810  according to the eighth embodiment is provided with a plurality of louvers  820 . The rest of the fin  810  except for the louvers  820  may have the same configuration as that of the fourth embodiment. For example, the louvers  820  may be provided to a second guide part  815 , that is, second slopes  817  as illustrated in  FIGS. 16 and 17 . 
     Referring to  FIGS. 18 and 19 , a fin  910  according to the ninth embodiment has the same configuration as that of the fifth embodiment except for louvers  920 . Referring to  FIGS. 20 and 21 , a fin  1010  according to the tenth embodiment has the same configuration as that of the sixth embodiment except for louvers  1020 . That is, the ninth and tenth embodiments may be suggested by adding the louvers  920  and  1020  to the fifth and sixth embodiments. According to the ninth embodiment, a second guide part  915  includes first to fourth slopes  916 ,  917 ,  918 , and  919 , and the louvers  920  may be provided to the second guide part  915 , substantially, to only the second and fourth slopes  917  and  919 . In a same manner, according to the tenth embodiment, a second guide part  1015  includes first to fourth slopes  1016 ,  1017 ,  1018 , and  1019 , and the louvers  1020  may be provided to the second guide part  1017 , substantially, to only the second and fourth slopes  1017  and  1019 . 
     According to the above embodiments, the second line passing through the center of the through hole is used to describe the position of each slope constituting the condensate water discharge part. Thus, when the center of the width of the through hole is aligned with the center of the width of the fin, the second line passes through the center of the width of the fin. 
     Although embodiments have been described with reference to a number of illustrative embodiments thereof, it should be understood that numerous other modifications and embodiments can be devised by those skilled in the art that will fall within the spirit and scope of the principles of this disclosure. More particularly, various variations and modifications are possible in the component parts and/or arrangements of the subject combination arrangement within the scope of the disclosure, the drawings and the appended claims. In addition to variations and modifications in the component parts and/or arrangements, alternative uses will also be apparent to those skilled in the art.