Patent Publication Number: US-2022236012-A1

Title: Heat exchanger and refrigeration cycle apparatus

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     The present application is a divisional application of U.S. utility application Ser. No. 16/627,550 filed on Dec. 30, 2019, which is a U.S. national stage application of PCT/JP2017/028257 filed on Aug. 3, 2017, the contents of which are incorporated herein by reference. 
    
    
     TECHNICAL FIELD 
     The present invention relates to a heat exchanger including a plurality of heat transfer pipes, and a refrigeration cycle apparatus including the heat exchanger. 
     BACKGROUND 
     There has hitherto been known a heat exchanger having the following configuration for improving heat exchange efficiency between refrigerant flowing through heat transfer pipes and an outside air. Specifically, a plurality of heat transfer pipes each having a flat shape are arranged so that a width direction thereof extends along a direction of an air stream, and projecting portions project along the direction of the air stream from both ends of each of the heat transfer pipes in the width direction (see, for example, Patent Literature 1). 
     PATENT LITERATURE 
     [PTL 1] JP 2008-202896 A 
     In the related-art heat exchanger disclosed in Patent Literature 1, however, the heat transfer pipe and the projecting portion are formed of an integrated single member. Thus, an integrated shape of the heat transfer pipe and the projecting portion is complicated, with the result that time and effort are required for manufacturing work for the heat transfer pipes and the projecting portions. 
     SUMMARY 
     The present invention has been made to solve the problem described above, and has an object to provide a heat exchanger, which can be improved in heat exchange performance and can easily be manufactured. 
     According to one embodiment of the present invention, there is provided a heat exchanger, including a plurality of heat exchange members arranged in a first direction so as to be spaced apart from each other, wherein each of the plurality of heat exchange members includes: a heat transfer pipe extending in a second direction intersecting with the first direction; and a heat transfer plate provided to the heat transfer pipe along the second direction, wherein the heat transfer plate includes extending portions extending away from the heat transfer pipe in a third direction intersecting with each of the first direction and the second direction, and wherein the heat transfer plate is a member formed separately from the heat transfer pipe. 
     With the heat exchanger and the refrigeration cycle apparatus according to one embodiment of the present invention, a heat transfer area of each of the heat exchange members to be brought into contact with an air stream can be increased with the presence of the extending portion to thereby improve heat exchange performance of the heat exchanger. Further, the heat transfer pipe and the heat transfer plate can be manufactured separately, and hence a shape of the heat transfer pipe and a shape of the heat transfer plate can be simplified. As a result, the heat exchanger can easily be manufactured. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1  is a schematic configuration diagram for illustrating an air conditioning apparatus according to a first embodiment of the present invention. 
         FIG. 2  is a perspective view for illustrating an outdoor heat exchanger of  FIG. 1 . 
         FIG. 3  is a perspective view for illustrating a state in which heat exchange members of  FIG. 2  are cut. 
         FIG. 4  is a sectional view for illustrating the heat exchange members of  FIG. 3 . 
         FIG. 5  is a perspective view for illustrating a lower part of a heat exchanger main body of  FIG. 1 . 
         FIG. 6  is a longitudinal sectional view for illustrating the lower part of the heat exchanger main body of  FIG. 5 . 
         FIG. 7  is a sectional view taken along the line VII-VII of  FIG. 6 . 
         FIG. 8  is a front view for illustrating a state in which dew condensation water adheres to the heat exchange members of  FIG. 3 . 
         FIG. 9  is a perspective view for illustrating a state in which heat exchange members of an outdoor heat exchanger according to a second embodiment of the present invention are cut. 
         FIG. 10  is a sectional view for illustrating the heat exchange members of  FIG. 9 . 
         FIG. 11  is a perspective view for illustrating a state in which heat exchange members of an outdoor heat exchanger according to a third embodiment of the present invention are cut. 
         FIG. 12  is a sectional view for illustrating the heat exchange members of  FIG. 11 . 
         FIG. 13  is a sectional view for illustrating a flow of an air stream passing between the plurality of heat exchanger members of  FIG. 12 . 
         FIG. 14  is a sectional view for illustrating another example of the heat exchange members of the outdoor heat exchanger according to the third embodiment of the present invention. 
         FIG. 15  is a sectional view for illustrating heat exchange members of an outdoor heat exchanger according to a fourth embodiment of the present invention. 
         FIG. 16  is a perspective view for illustrating a state in which heat exchange members of an outdoor heat exchanger according to a fifth embodiment of the present invention are cut. 
         FIG. 17  is a sectional view for illustrating the heat exchange members of  FIG. 16 . 
         FIG. 18  is a perspective view for illustrating a state in which the heat exchange members of another example of the outdoor heat exchanger according to the fifth embodiment of the present invention are cut. 
         FIG. 19  is a sectional view for illustrating the heat exchange members of  FIG. 18 . 
         FIG. 20  is a perspective view for illustrating a state in which the heat exchange members of another example of the outdoor heat exchanger according to the fifth embodiment of the present invention are cut. 
         FIG. 21  is a sectional view for illustrating the heat exchange members of  FIG. 20 . 
         FIG. 22  is a sectional view for illustrating heat exchange members of an outdoor heat exchanger according to a sixth embodiment of the present invention. 
         FIG. 23  is a front view for illustrating a main part of a heat exchanger main body of an outdoor heat exchanger according to a seventh embodiment of the present invention. 
         FIG. 24  is a perspective view for illustrating an outdoor heat exchanger according to an eighth embodiment of the present invention. 
     
    
    
     DETAILED DESCRIPTION 
     Now, preferred embodiments of the present invention are described with reference to the accompanying drawings. 
     First Embodiment 
       FIG. 1  is a schematic configuration diagram for illustrating a refrigeration cycle apparatus according to a first embodiment of the present invention. In this embodiment, the refrigeration cycle apparatus is used as an air conditioning apparatus  1 . The air conditioning apparatus  1  includes a compressor  2 , an outdoor heat exchanger  3 , an expansion valve  4 , an indoor heat exchanger  5 , and a four-way valve  6 . In this example, the compressor  2 , the outdoor heat exchanger  3 , the expansion valve  4 , and the four-way valve  6  are provided to an outdoor unit. The indoor heat exchanger  5  is provided to an indoor unit. 
     The compressor  2 , the outdoor heat exchanger  3 , the expansion valve  4 , the indoor heat exchanger  5 , and the four-way valve  6  are connected to each other through refrigerant pipes to form a refrigerant circuit through which the refrigerant can circulate. In the air conditioning apparatus  1 , a refrigeration cycle in which the refrigerant circulates through the compressor  2 , the outdoor heat exchanger  3 , the expansion valve  4 , and the indoor heat exchanger  5  while being changed in phase is performed by drive of the compressor  2 . 
     An outdoor fan  7  configured to force an outdoor air to pass through the outdoor heat exchanger  3  is provided to the outdoor unit. The outdoor heat exchanger  3  exchanges heat between an air stream of the outdoor air, which is generated by an operation of the outdoor fan  7 , and the refrigerant. An indoor fan  8  configured to force an indoor air to pass through the indoor heat exchanger  5  is provided to the indoor unit. The indoor heat exchanger  5  exchanges heat between an air stream of the indoor air, which is generated by an operation of the indoor fan  8 , and the refrigerant. 
     An operation of the air conditioning apparatus  1  can be switched between a cooling operation and a heating operation. The four-way valve  6  is an electromagnetic valve configured to switch a refrigerant flow passage in accordance with the switching between the cooling operation and the heating operation of the air conditioning apparatus  1 . The four-way valve  6  guides the refrigerant from the compressor  2  to the outdoor heat exchanger  3  and the refrigerant from the indoor heat exchanger  5  to the compressor  2  during the cooling operation, and guides the refrigerant from the compressor  2  to the indoor heat exchanger  5  and the refrigerant from the outdoor heat exchanger  3  to the compressor  2  during the heating operation. In  FIG. 1 , a direction of a flow of the refrigerant during the cooling operation is indicated by the broken-line arrow, and a direction of a flow of the refrigerant during the heating operation is indicated by the solid-line arrow. 
     During the cooling operation of the air conditioning apparatus  1 , the refrigerant compressed by the compressor  2  is sent to the outdoor heat exchanger  3 . In the outdoor heat exchanger  3 , the refrigerant rejects heat to the outdoor air and is condensed. After that, the refrigerant is sent to the expansion valve  4 . After being decompressed by the expansion valve  4 , the refrigerant is sent to the indoor heat exchanger  5 . Then, after the refrigerant takes heat from the indoor air and evaporates in the indoor heat exchanger  5 , the refrigerant returns to the compressor  2 . Thus, during the cooling operation of the air conditioning apparatus  1 , the outdoor heat exchanger  3  functions as a condenser, and the indoor heat exchanger  5  functions as an evaporator. 
     During the heating operation of the air conditioning apparatus  1 , the refrigerant compressed by the compressor  2  is sent to the indoor heat exchanger  5 . In the indoor heat exchanger  5 , the refrigerant rejects heat to the indoor air and is condensed. After that, the refrigerant is sent to the expansion valve  4 . After being decompressed by the expansion valve  4 , the refrigerant is sent to the outdoor heat exchanger  3 . Then, after the refrigerant takes heat from the outdoor air and evaporates in the outdoor heat exchanger  3 , the refrigerant returns to the compressor  2 . Thus, during the heating operation of the air conditioning apparatus  1 , the outdoor heat exchanger  3  functions as an evaporator, and the indoor heat exchanger  5  functions as a condenser. 
       FIG. 2  is a perspective view for illustrating the outdoor heat exchanger  3  of  FIG. 1 . The outdoor heat exchanger  3  includes a heat exchanger main body  11  through which an air stream A generated by the operation of the outdoor fan  7  passes. The heat exchanger main body  11  includes a first header tank  12 , a second header tank  13 , and a plurality of heat exchange members  14 , which connect the first header tank  12  and the second header tank  13  to each other. In the heat exchanger main body  11 , one of a refrigerant pipe from the expansion valve  4  and a refrigerant pipe from the four-way valve  6  is connected to the first header tank  12 , and another one is connected to the second header tank  13 . 
     Each of the first header tank  12  and the second header tank  13  is horizontally arranged. Further, the second header tank  13  is arranged above the first header tank  12 . The first header tank  12  and the second header tank  13  are arranged so as to be parallel to each other along a z direction of  FIG. 2 , which is a first direction. 
     The plurality of heat exchange members  14  are arranged so as to be spaced apart from each other in a longitudinal direction of each of the first header tank  12  and the second header tank  13 , specifically, in the z direction of  FIG. 2 . Further, the plurality of heat exchange members  14  are arranged in parallel to each other. A longitudinal direction of the plurality of heat exchange members  14  matches with a second direction intersecting with the z direction of  FIG. 2 , which is the first direction. In this example, the second direction is a y direction of  FIG. 2 , which is orthogonal to the z direction of  FIG. 2 . The longitudinal direction of each of the heat exchange members  14  is orthogonal to the longitudinal direction of each of the first header tank  12  and the second header tank  13 . In this example, arrangement of a member in a space between the plurality of heat exchange members  14  is prohibited. With the arrangement described above, in this example, connection of a member to surfaces of adjacent ones of the heat exchange members  14 , which are opposed to each other, is avoided. 
     The air stream A generated by the operation of the outdoor fan  7  passes between the plurality of heat exchange members  14 . In this example, the air stream A passes between the plurality of heat exchange members  14  along a direction orthogonal to the longitudinal direction of the first header tank  12  and the second header tank  13  and the longitudinal direction of each of the heat exchange members  14 , specifically, along an x direction of  FIG. 2 . 
       FIG. 3  is a perspective view for illustrating a state in which the heat exchange members  14  of  FIG. 2  are cut.  FIG. 4  is a sectional view for illustrating the heat exchange members  14  of  FIG. 3 . Each of the plurality of heat exchange members  14  includes a heat transfer pipe  15 , a heat transfer plate  16 , and a joining member  17 . The heat transfer pipe  15  extends in the y direction being the second direction. The heat transfer plate  16  is provided to the heat transfer pipe  15  along a longitudinal direction of the heat transfer pipe  15 , specifically, the second direction. The joining member  17  is provided between the heat transfer pipe  15  and the heat transfer plate  16 , and is configured to join the heat transfer plate  16  to the heat transfer pipe  15 . 
     A sectional shape of the heat transfer pipe  15  cut along a plane orthogonal to the longitudinal direction of the heat transfer pipe  15  is a flat shape having a long axis and a short axis. Thus, when a long axis direction of a cross section of the heat transfer pipe  15  is set as a width direction of the heat transfer pipe  15 , and a short axis direction of the cross section of the heat transfer pipe  15  is set as a thickness direction of the heat transfer pipe  15 , a dimension of the heat transfer pipe  15  in the width direction is larger than a dimension of the heat transfer pipe  15  in the thickness direction. Each of the heat transfer pipes  15  is arranged in a state in which the thickness direction of the heat transfer pipe  15  matches with a direction in which the plurality of heat transfer pipes  15  are arranged, specifically, the z direction, and the width direction of the heat transfer pipe  15  matches with a direction of the air stream A, specifically, the x direction. 
     A plurality of refrigerant flow passages  18  through which the refrigerant flows are arranged inside the heat transfer pipe  15  along the longitudinal direction of the heat transfer pipe  15 . The plurality of refrigerant flow passages  18  are arranged side by side in the width direction of the heat transfer pipe  15 . In the heat exchange member  14 , heat is exchanged between the air stream A passing between the plurality of heat exchange members  14  and the refrigerant flowing through the refrigerant flow passages  18 . 
     The heat transfer pipe  15  is made of a metal material having heat conductivity. As the material for forming the heat transfer pipe  15 , for example, aluminum, an aluminum alloy, copper, or a copper alloy is used. The heat transfer pipe  15  is manufactured by extrusion for extruding a heated material through a hole of a die to form the cross section of the heat transfer pipe  15 . The heat transfer pipe  15  may be manufactured by drawing for drawing a material through a hole of a die to form the cross section of the heat transfer pipe  15 . 
     The heat transfer plate  16  is a member formed separately from the heat transfer pipe  15 . Further, the heat transfer plate  16  is arranged along a third direction, which intersects with the z direction being the first direction and the y direction being the second direction. In this example, the third direction is the x direction orthogonal to each of the z direction and the y direction. The heat transfer plate  16  is a flat plate arranged along the x direction. The heat exchanger main body  11  is arranged so that the direction of the air stream A matches with the x direction. A dimension of the heat transfer plate  16  in the thickness direction is smaller than a dimension of the heat transfer pipe  15  in the thickness direction. The heat transfer plate  16  is made of a metal material having heat conductivity. As the material for forming the heat transfer plate  16 , for example, aluminum, an aluminum alloy, copper, or a copper alloy is used. 
     The heat transfer plate  16  includes one extending portion  162 , another extending portion  163 , and a heat transfer plate main body portion  161 . The one extending portion  162  and the another extending portion  163  extend away from the heat transfer pipe  15  on both sides of the heat transfer pipe  15  in the x direction being the third direction. The heat transfer plate main body portion  161  is continuous with the one extending portion  162  and the another extending portion  163 . The heat transfer plate main body portion  161  overlaps an outer peripheral surface of the heat transfer pipe  15 . The one extending portion  162  extends from the heat transfer plate main body portion  161  toward an upstream side of the air stream A with respect to the heat transfer pipe  15 . The another extending portion  163  extends from the heat transfer plate main body portion  161  toward a downstream side of the air stream A with respect to the heat transfer pipe  15 . In this example, a dimension of the extending portion  162  on the upstream side is larger than a dimension of the extending portion  163  on the downstream side in the x direction. 
     The heat transfer plate main body portion  161  overlaps a portion of the outer peripheral surface of the heat transfer pipe  15 , which extends along the width direction of the heat transfer pipe  15 , through the joining member  17  therebetween. The extending portion  162  on the upstream side and the extending portion  163  on the downstream side are present outside a region of the heat transfer pipe  15  in the width direction of the heat transfer pipe  15  when viewed along the thickness direction of the heat transfer pipe  15 , specifically, the z direction. 
     The joining member  17  is made of a metal material having heat conductivity. As the material for forming the joining member  17 , for example, aluminum, an aluminum alloy, copper, or a copper alloy is used. In this example, a brazing filler metal is used for the joining member  17 . A melting point of the material for forming the joining member  17  is set lower than a melting point of the material for forming the heat transfer pipe  15  and a melting point of the material for forming the heat transfer plate  16 . 
       FIG. 5  is a perspective view for illustrating a lower part of the heat exchanger main body  11  of  FIG. 1 .  FIG. 6  is a longitudinal sectional view for illustrating the lower part of the heat exchanger main body  11  of  FIG. 5 .  FIG. 7  is a sectional view taken along the line VII-VII of  FIG. 6 . The first header tank  12  has a plurality of insertion holes  121  passing through an upper wall portion of the first header tank  12 . The second header tank  13  has a plurality of insertion holes (not shown) passing through a lower wall portion of the second header tank  13 . The plurality of insertion holes  121  formed in the first header tank  12  and the second header tank  13  are formed so as to be matched with positions of the plurality of heat exchange members  14 . 
     In each of the heat exchange members  14 , both end portions  15   a  of the heat transfer pipe  15  in the longitudinal direction project from the heat transfer plate  16 . One end portion  15   a  of the heat transfer pipe  15  in the longitudinal direction is inserted into a space inside the first header tank  12  in a state of being inserted through the insertion hole  121  of the first header tank  12 , and another end portion  15   a  of the heat transfer pipe  15  in the longitudinal direction is inserted into a space inside the second header tank  13  in a state of being inserted through the insertion hole of the second header tank  13 . Specifically, only the one end portion  15   a  of the heat transfer pipe  15  of the heat exchange member  14  in the longitudinal direction is inserted into the space inside the first header tank  12 , and only the another end portion  15   a  of the heat transfer pipe  15  of the heat exchange member  14  in the longitudinal direction is inserted into the space inside the second header tank  13 . In this manner, the space inside the first header tank  12  and the space inside the second header tank  13 , and the refrigerant flow passages  18  of the heat transfer pipes  15  are brought into communication with each other. Each of the heat transfer pipes  15  is connected to the first header tank  12  and the second header tank  13  by, for example, brazing or welding. A refrigerant B flows through the first header tank  12 , the refrigerant flow passages  18 , and the second header tank  13  in the started order or through the second header tank  13 , the refrigerant flow passages  18 , and the first header tank  12  in the started order in accordance with the cooling operation and the heating operation. 
     In the heat exchanger main body  11 , heat is exchanged between the air stream A generated by the operation of the outdoor fan  7  and the refrigerant B flowing through the refrigerant flow passages  18  of the heat transfer pipes  15 . Thus, heat exchange performance of the heat exchanger main body  11  is improved as an area of each of the heat exchange members  14 , with which the air stream A comes into contact, increases. 
     When the outdoor heat exchanger  3  functions as a condenser, the refrigerant B having a temperature higher than a temperature of the air stream A flows through the refrigerant flow passages  18 . Thus, when the outdoor heat exchanger  3  functions as a condenser, heat is rejected from the refrigerant B to the air stream A. 
     When the outdoor heat exchanger  3  functions as an evaporator, the refrigerant B having a temperature lower than a temperature of the air stream A flows through the refrigerant flow passages  18 . Thus, when the outdoor heat exchanger  3  functions as an evaporator, heat is taken from the air stream A into the refrigerant B. On this occasion, dew condensation water is sometimes generated on a surface of the heat exchange member  14 . 
       FIG. 8  is a front view for illustrating a state in which dew condensation water adheres to the heat exchange members  14  of  FIG. 3 . Dew condensation water  10  adhering to the surface of each of the heat exchange members  14  moves downward by its own weight along the surface of each of the heat exchange members  14 . On this occasion, no member is connected to the surface of each of the heat exchange members  14 , and hence the downward movement of the dew condensation water  10  is not inhibited by a member. As a result, the dew condensation water  10  is easily discharged downward. 
     The heat exchanger main body  11  is manufactured by heating an assembled body including the heat transfer pipes  15 , the heat transfer plates  16 , the first header tank  12 , and the second header tank  13  in a furnace. A brazing filler metal is applied in advance to the surface of each of the heat transfer pipes  15  and the surface of each of the heat transfer plates  16 . The heat transfer pipes  15 , the heat transfer plates  16 , the first header tank  12 , and the second header tank  13  are fixed to each other with the brazing filler metal molten by heating in the furnace. The brazing filler metal is provided as the joining member  17  between each pair of the heat transfer pipe  15  and the heat transfer plate  16 . 
     In the outdoor heat exchanger  3  described above, each of the heat transfer plates  16  includes the extending portions  162  and  163 , which extend away from the heat transfer pipe  15  in the x direction being the third direction. Thus, a heat transfer area of each of the heat exchange members  14 , which is brought into contact with the air stream A, can be increased with the presence of the extending portions  162  and  163 . Thus, the heat exchange performance of the outdoor heat exchanger  3  can be improved. Further, the heat transfer plate  16  is a member formed separately from the heat transfer pipe  15 . Thus, the heat transfer pipe  15  and the heat transfer plate  16  can be manufactured separately from each other. Thus, a shape of the heat transfer pipe  15  and a shape of the heat transfer plate  16  can be simplified. In this manner, each of the heat transfer pipe  15  and the heat transfer plate  16  can easily be manufactured. Thus, the outdoor heat exchanger  3  can easily be manufactured. 
     The end portions  15   a  of the heat transfer pipe  15  in the longitudinal direction project from the heat transfer plate  16 . Further, the end portions  15   a  of the heat transfer pipe  15  in the longitudinal direction are inserted into the space inside the first header tank  12  and the space inside the second header tank  13 , respectively. Accordingly, a shape of each of the insertion holes  121  through which the heat exchange members  14  are inserted can be formed so as to be matched with a shape of the outer peripheral surface of each of the heat transfer pipes  15 . As a result, complication of the shape of each of the insertion holes  121  can be prevented. In this manner, connection work for the heat exchange members  14  to the first header tank  12  and the second header tank  13  can easily be performed. Thus, the heat exchanger main body  11  can more easily be manufactured. 
     Second Embodiment 
     In the first embodiment, the flat pipe having the flat sectional shape is used as the heat transfer pipe  15 . However, a circular pipe having a circular sectional shape may be used as the heat transfer pipe  15 . 
       FIG. 9  is a perspective view for illustrating a state in which the heat exchange members  14  of the outdoor heat exchanger  3  according to a second embodiment of the present invention are cut.  FIG. 10  is a sectional view for illustrating the heat exchange members  14  of  FIG. 9 . In this embodiment, the sectional shape of each of the heat transfer pipes  15  is circular. Further, in this embodiment, one refrigerant flow passage  18  is formed in one heat transfer pipe  15 . Other configurations are the same as those of the first embodiment. 
     As described above, even when the circular pipes, each having the circular sectional shape, are used as the heat transfer pipes  15 , as in the first embodiment, a heat transfer area of each of the heat exchange members  14  can be increased with the presence of the extending portions  162  and  163 . Thus, the heat exchange performance of the outdoor heat exchanger  3  can be improved. Further, the heat transfer plate  16  is a member formed separately from the heat transfer pipe  15 . Thus, as in the first embodiment, the shape of the heat transfer pipe  15  and the shape of the heat transfer plate  16  can be simplified. As a result, the outdoor heat exchanger  3  can easily be manufactured. 
     Third Embodiment 
       FIG. 11  is a perspective view for illustrating a state in which the heat exchange members  14  of the outdoor heat exchanger  3  according to a third embodiment of the present invention are cut.  FIG. 12  is a sectional view for illustrating the heat exchange members  14  of  FIG. 11 . An outer peripheral surface of each of the heat transfer pipes  15  includes a first thickness-direction end surface  151 , a second thickness-direction end surface  152 , an upstream-side end surface  153 , and a downstream-side end surface  154 . The first thickness-direction end surface  151  and the second thickness-direction end surface  152  are opposed to each other in the thickness direction of the heat transfer pipe  15 . The upstream-side end surface  153  and the downstream-side end surface  154  are opposed to each other in the width direction of the heat transfer pipe  15 . The heat transfer pipe  15  is arranged so that the upstream-side end surface  153  is oriented toward an upstream side of the air stream A with respect to the downstream-side end surface  154 . 
     The heat transfer plate main body portion  161  overlaps the first thickness-direction end surface  151  of the heat transfer pipe  15 . An end portion of the heat transfer plate main body portion  161  on the upstream side in a direction of the air stream A is a curved portion  161   a  that covers the outer peripheral surface of the heat transfer pipe  15 . Thus, the curved portion  161   a  of the heat transfer plate main body portion  161  covers the upstream-side end surface  153  of the heat transfer pipe  15 . The joining member  17  is provided between the first thickness-direction end surface  151  and the heat transfer plate main body portion  161  and between the upstream-side end surface  153  of the heat transfer pipe  15  and the heat transfer plate main body portion  161 . The curved portion  161   a  of the heat transfer plate main body portion  161  is more gently inclined than the upstream-side end surface  153  of the heat transfer pipe  15  with respect to the direction of the air stream A. 
     The second thickness-direction end surface  152  and the downstream-side end surface  154  of the heat transfer pipe  15  are exposed to the outside. The extending portion  162  of the heat transfer plate  16  on the upstream side extends from an end of the curved portion  161   a  toward the upstream side of the air stream A. The extending portion  162  of the heat transfer plate  16  on the upstream side is arranged in alignment with a position of the second thickness-direction end surface  152  of the heat transfer pipe  15  in the thickness direction of the heat transfer pipe  15 . 
       FIG. 13  is a sectional view for illustrating a flow of the air stream A passing between the plurality of heat exchange members  14  of  FIG. 12 . The air stream A passing between the plurality of heat exchange members  14  flows along surfaces of the heat exchange members  14  as indicated by the arrows in  FIG. 13 . Thus, the air stream A, which has reached the heat transfer plate main body portion  161  from the extending portion  162  on the upstream side, smoothly flows along a surface of the curved portion  161   a  without colliding against the upstream-side end surface  153  of the heat transfer pipe  15 . Further, the air stream A, which has reached the second thickness-direction end surface  152  of the heat transfer pipe  15  from the extending portion  162  on the upstream side, directly flows along the second thickness-direction end surface  152 . As a result, a resistance to the flow of the air stream A when the air stream A passes between the plurality heat exchange members  14  is reduced. Other configurations are the same as those of the first embodiment. 
     In the outdoor heat exchanger  3 , each of the heat transfer plates  16  has the curved portion  161   a  that covers the outer peripheral surface of the heat transfer pipe  15 . The extending portion  162  on the upstream side extends from the end of the curved portion  161   a . Thus, the air stream A can smoothly flow along the curved portion  161   a . In this manner, the resistance to the flow of the air stream A passing between the plurality of heat exchange members  14  can be reduced. In addition, a heat transfer area between the outer peripheral surface of the heat transfer pipe  15  and the heat transfer plate main body portion  161  can be increased. Thus, the heat exchange performance of the outdoor heat exchanger  3  can be further increased. Further, when the heat transfer pipe  15  and the heat transfer plate  16  are combined, a position of the heat transfer plate  16  with respect to the heat transfer pipe  15  can easily be specified based on a position of the curved portion  161   a . In this manner, the outdoor heat exchanger  3  can more easily be manufactured. 
     In the example described above, the extending portion  162  on the upstream side is arranged in alignment with the position of the second thickness-direction end surface  152  of the heat transfer pipe  15  in the thickness direction of the heat transfer pipe  15 . However, the extending portion  162  on the upstream side may be arranged so as to be shifted in the thickness direction of the heat transfer pipe  15  with respect to the position of the second thickness-direction end surface  152  of the heat transfer pipe  15 . Even with the arrangement described above, the air stream A can smoothly flow along the curved portion  161   a . Thus, the resistance to the flow of the air stream A passing between the plurality of heat exchange members  14  can be reduced. 
     In the example described above, only the end portion of the heat transfer plate main body portion  161  on the upstream side in the direction of the air stream A is formed as the curved portion  161   a . However, as illustrated in  FIG. 14 , the end portions of the heat transfer plate main body portion  161  on the upstream side and the downstream side in the direction of the air stream A may be formed as the curved portion  161   a  and a curved portion  161   b , respectively. In this case, the curved portion  161   a  of the heat transfer plate main body portion  161  on the upstream side covers the upstream-side end surface  153  of the heat transfer pipe  15 , and the curved portion  161   b  of the heat transfer plate main body portion  161  on the downstream side covers the downstream-side end surface  154  of the heat transfer pipe  15 . Further, in this case, the extending portion  162  on the upstream side extends from the end of the curved portion  161   a  on the upstream side, and the extending portion  163  on the downstream side extends from an end of the curved portion  161   b  on the downstream side. Further, in this case, the extending portion  162  on the upstream side and the extending portion  163  on the downstream side are arranged in alignment with the position of the second thickness-direction end surface  152  of the heat transfer pipe  15  in the thickness direction of the heat transfer pipe  15 . 
     Fourth Embodiment 
       FIG. 15  is a sectional view for illustrating the heat transfer members  14  of the outdoor heat exchanger  3  according to a fourth embodiment of the present invention. The end portions of the heat transfer plate main body portion  161  on the upstream side and the downstream side in the direction of the air stream A are formed as the curved portion  161   a  and  161   b , which cover the outer peripheral surface of the heat transfer pipe  15 . The curved portion  161   a  of the heat transfer plate main body portion  161  on the upstream side covers the upstream-side end surface  153  of the heat transfer pipe  15 , and the curved portion  161   b  of the heat transfer plate main body portion  161  on the downstream side covers the downstream-side end surface  154  of the heat transfer pipe  15 . 
     The heat transfer pipe  15  is held between the curved portions  161   a  and  161   b  under a state in which the curved portions  161   a  and  161   b  of the heat transfer plate main body portion  161  on the upstream side and the downstream side are elastically deformed. The curved portion  161   a  on the upstream side generates an elastic restoration force in a direction of pressing the end of the heat transfer pipe  15  on the upstream side, and the curved portion  161   b  on the downstream side generates an elastic restoration force in a direction of pressing the end of the heat transfer pipe  15  on the downstream side. In this manner, the heat transfer plate  16  is held on the heat transfer pipe  15  under a state in which the heat transfer plate main body portion  161  is held in contact with the outer peripheral surface of the heat transfer pipe  15 . In this example, the joining member  17  is not provided between the outer peripheral surface of the heat transfer pipe  15  and the heat transfer plate main body portion  161 . 
     When the heat transfer member  14  is manufactured, the heat transfer pipe  15  is inserted between the curved portion  161   a  on the upstream side and the curved portion  161   b  on the downstream side under a state in which the curved portions  161   a  and  161   b  are elastically deformed in a direction in which the curved portions  161   a  and  161   b  are separated away from each other. After that, the elastic deformation of the curved portions  161   a  and  161   b  is restored. In this manner, the heat transfer pipe  15  is held between the curved portions  161   a  and  161   b  to fix the heat transfer plate  16  to the heat transfer pipe  15 . The heat exchange member  14  is completed after the fixation of the heat transfer plate  16  to the heat transfer pipe  15 . Other configurations are the same as those of the first embodiment. 
     In the outdoor heat exchanger  3  described above, the heat transfer pipe  15  is held between the curved portions  161   a  and  161   b  with the elastic restoration forces of the curved portions  161   a  and  161   b  of the heat transfer plate main body portion  161  on the upstream side and the downstream side. Hence, the need of the joining member  17  configured to join the heat transfer plate  16  to the heat transfer pipe  15  can be eliminated. As a result, the heat exchange member  14  can easily be manufactured. 
     Fifth Embodiment 
       FIG. 16  is a perspective view for illustrating a state in which the heat exchange members  14  of the outdoor heat exchanger  3  according to a fifth embodiment of the present invention are cut.  FIG. 17  is a sectional view for illustrating the heat exchange members  14  of  FIG. 16 . A plurality of cutout portions  21  serving as heat resistance portions configured to suppress heat conduction through the extending portion  162  on the upstream side are formed in the extending portion  162 . Each of the cutout portions  21  is a linear cut passing in the thickness direction of the extending portion  162 . In this example, the plurality of cutout portions  21  are formed in the extending portion  162  along the longitudinal direction of the heat transfer pipe  15 . Other configurations are the same as those of the first embodiment. 
     When the outdoor heat exchanger  3  functions as an evaporator, the heat exchange member  14  is sometimes frosted. A frosting amount on the heat exchange member  14  increases as a difference between a temperature of the refrigerant B flowing through the refrigerant flow passages  18  and a temperature of the air stream A becomes larger. When the frosting amount on the heat exchange member  14  increases, a space between the plurality of heat exchange members  14  is reduced due to the presence of frost. Thus, the air stream A is less likely to pass between the plurality of heat exchange members  14 . 
     In this embodiment, transfer of heat from the extending portion  162  to the heat transfer pipe  15  is suppressed with the presence of the plurality of cutout portions  21 . As a result, a decrease of the temperature of the extending portion  162  can be suppressed, and the heat transfer member  14  is less liable to be frosted. Further, even when the heat exchange member  14  is frosted, the frosting amount is small. 
     In the outdoor heat exchanger  3  described above, the plurality of cutout portions  21  serving as the heat resistance portions configured to suppress the heat conduction from a distal end of the extending portion  162  toward the heat transfer plate main body portion  161  are formed in the extending portion  162  on the upstream side. Thus, the decrease of the temperature of the extending portion  162  on the upstream side can be suppressed. In this manner, the increase of the difference between the temperature of the extending portion  162  and the temperature of the air stream A can be suppressed. As a result, the heat exchange members  14  becomes less liable to be frosted. 
     In the example described above, the plurality of cutout portions  21  are used as the heat resistance portions. However, the heat resistance portions are not limited thereto. For example, as illustrated in  FIG. 18  and  FIG. 19 , a plurality of cut-and-raised portions  22  may be used as the heat resistance portions. Each of the cut-and-raised portions  22  is a portion formed by deforming and raising a portion between two parallel cuts formed in the extending portion  162  in the thickness direction of the extending portion  162 . In this case, the plurality of cut-and-raised portions  22  are formed along the longitudinal direction of the heat transfer pipe  15 . 
     Further, for example, as illustrated in  FIG. 20  and  FIG. 21 , a plurality of louvers  23  may be used as the heat resistance portions. Each of the louvers  23  is formed by deforming a portion between two parallel cuts formed in the extending portion  162  and inclining the portion with respect to a surface of the extending portion  162 . In this case, the plurality of louvers  23  are formed along the longitudinal direction of the heat transfer pipe  15 . 
     In the example described above, the cutout portions  21 , the cut-and-raised portions  22 , or the louvers  23  serving as the heat resistance portions are applied to the heat exchange members  14  of the first embodiment. However, the cutout portions  21 , the cut-and-raised portions  22 , or the louvers  22  serving as the heat resistance portions may be applied to the heat exchange members  14  of the second to fourth embodiments. 
     Sixth Embodiment 
       FIG. 22  is a sectional view for illustrating the heat exchange members  14  of the outdoor heat exchanger  3  according to a sixth embodiment of the present invention. The heat exchanger main body  11  includes a plurality of first heat exchange members  32  and a plurality of second heat exchange members  34  as the plurality of heat exchange members. Configurations of the plurality of first heat exchange members  32  and the plurality of second heat exchange members  34  are the same as those of the heat exchange members  14  of the third embodiment. 
     The plurality of first heat exchange members  32  are arranged in a first line  31  so as to be spaced apart from each other. In the first line, the plurality of first heat exchange members  32  are arranged in the z direction. Each of the first heat exchange members  32  is arranged under a state in which the thickness direction of the heat transfer pipe  15  matches with the z direction. 
     The plurality of second heat exchange members  34  are arranged in a second line  33 , which is located at a position distant from the first line  31 , so as to be spaced apart from each other in the x direction. In this example, the second line  33  is located on the downstream side of the air stream A with respect to the first line  31 . In the second line  33 , the plurality of second heat exchange members  34  are arranged in the z direction. Each of the second heat exchange members  34  is arranged under a state in which the thickness direction of the heat transfer pipe  15  matches with the z direction. 
     The plurality of second heat exchange members  34  are arranged between the plurality of heat exchange members  32  when viewed along the x direction. Specifically, when the heat exchanger main body  11  is viewed along the x direction, overlapping of each of the second heat exchange members  34  with each of the first heat exchange members  32  is avoided. In this example, the first heat exchange members  32  and the second heat exchange members  34  are arranged at positions in a staggered pattern in which the first heat exchange members  32  and the second heat exchange members  34  are located alternately in the first line  31  and the second line  33  in the z direction. 
     The extending portion  162  of each of the second heat exchange members  34  on the upstream side is arranged in a space between the plurality of first heat exchange members  32 . The extending portion  163  of each of the first heat exchange members  32  on the downstream side is arranged in a space between the plurality of second heat exchange members  34 . With the arrangement described above, when the heat exchanger main body  11  is viewed along the z direction being a direction in which the plurality of first heat exchange members  32  and the plurality of second heat exchange members  34  are arranged, the extending portion  162  of each of the second heat exchange members  34  on the upstream side overlaps a downstream-side portion of the first heat exchange member  32 , and the extending portion  163  of each of the first heat exchange members  32  on the downstream side overlaps an upstream-side portion of the second heat exchange member  34 . Other configurations are the same as those of the third embodiment. 
     In the outdoor heat exchanger  3  described above, when viewed along the x direction, the plurality of second heat exchange members  34  are arranged between the plurality of first heat exchange members  32 . Thus, the extending portions  162  of the second heat exchange members  34  arranged in the second line  33  can extend toward the first line  31  so as to avoid the first heat exchange members  32 . Further, the extending portions  163  of the first heat exchange members  32  can extend toward the second line  33  so as to avoid the second heat exchange members  34 . Further, portions of the second heat exchange members  34  on a side closer to the first line  31  can be inserted between portions of the plurality of first heat exchange members  32  on a side closer to the second line  33 . Thus, an increase in dimensions of the heat exchanger main body  11  in the x direction can be suppressed. Further, the heat transfer plate  16  is formed separately from the heat transfer pipe  15 . As a result, a thickness of the heat transfer plate  16  can be reduced. Thus, even when the extending portion  162  of the second heat exchange member  34  on the upstream side is inserted between the plurality of first heat exchange members  32 , reduction of flow passages for the air stream A can be suppressed. In this manner, a heat transfer area of each of the first heat transfer members  32  and a heat transfer area of each of the second heat transfer members  34  for the air stream A can be increased while increase in size of the heat exchanger main body  11  is suppressed. Hence, the heat exchange performance of the heat exchanger main body  11  can be further improved. 
     In the example described above, the heat exchange members are arranged in two lines including the first line  31  and the second line  33 . However, the number of lines in which the heat exchange members are arranged is not limited to two, and may be three or more. In this case, the plurality of heat exchange members arranged in one of two lines adjacent to each other are arranged between the plurality of heat exchange members arranged in another one of the lines. 
     Further, in the example described above, the extending portion  162  and the extending portion  163  project from the heat transfer plate main body portion  161  of each of the first heat exchange members  32  toward the upstream side and the downstream side of the air stream A, respectively. However, the extending portion  162  may project from the heat transfer plate main body portion  161  of each of the first heat exchange members  32  only toward the upstream side, which is one of the upstream side and the downstream side of the air stream A, or the extending portion  163  may project from the heat transfer plate main body portion  161  only toward the downstream side, which is one of the upstream side and the downstream side of the air stream A. 
     Further, in the example described above, the extending portion  162  and the extending portion  163  project from the heat transfer plate main body portion  161  of each of the second heat exchange members  34  toward the upstream side and the downstream side of the air stream A, respectively. However, the extending portion  162  may project from the heat transfer plate main body portion  161  of each of the second heat exchange members  34  only toward the upstream side, which is one of the upstream side and the downstream side of the air stream A, or the extending portion  163  may project from the heat transfer plate main body portion  161  only toward the downstream side, which is one of the upstream side and the downstream side of the air stream A. 
     Further, in the example described above, the configuration of each of the heat exchange members  14  of the third embodiment is applied to each of the first heat exchange members  32 . However, the configuration of each of the heat exchange members  14  of the first, second, fourth, or fifth embodiment may be applied to each of the first heat exchange members  32 . 
     Further, in the example described above, the configuration of each of the heat exchange members  14  of the third embodiment is applied to each of the second heat exchange members  34 . However, the configuration of each of the heat exchange members  14  of the first, second, fourth, or fifth embodiment may be applied to each of the second heat exchange members  34 . 
     Seventh Embodiment 
       FIG. 23  is a front view for illustrating a main part of the heat exchanger main body  11  of the outdoor heat exchanger  3  according to a seventh embodiment of the present invention. The heat exchanger main body  11  includes the plurality of heat exchange members  14  and heat transfer fins  41 , each being connected between two adjacent ones of the heat exchange members  14 . Arrangement and configuration of the plurality of heat exchange members  14  are the same as those of the first embodiment. 
     In this example, a corrugated fin formed in a corrugated shape is used as each of the heat transfer fins  41 . Further, in this example, each of the heat transfer fins  41  is connected only to a portion of each of the heat exchange members  14  on the downstream side in the direction of the air stream A, specifically, in the x direction. As a material for forming the heat transfer fins  41 , for example, aluminum, an aluminum alloy, copper, or a copper alloy is used. Other configurations are the same as those of the first embodiment. 
     In the outdoor heat exchanger  3  described above, each of the heat transfer fins  41  is connected between two adjacent ones of the heat exchange members  14 . Thus, a heat transfer area of the heat exchange main body  11  for the air stream A can be further increased with the presence of the heat transfer fins  41 . In this manner, the heat exchange performance of the heat exchanger main body  11  can be further improved. 
     Further, the heat transfer fin  41  is connected only to the portion of the heat exchange member  14  on the downstream side in the direction of the air stream A. Thus, the heat transfer fins  41  can be arranged so as to avoid portions of the heat exchange members  14  on the upstream side, which are liable to be frosted. In this manner, reduction in heat transfer performance of the heat transfer fins  41  due to frosting can be suppressed. 
     In the example described above, the heat transfer fin  41  is connected to only part of each of the heat exchange members  14  in the direction of the air stream A. However, the heat transfer fin  41  may be connected to the entire region of each of the heat exchange members  14  in the direction of the air stream A. 
     In the example described above, the heat transfer fins  41  are applied to the heat exchanger main body  11  of the first embodiment. However, the heat transfer fins  41  may be applied to the heat exchanger main body  11  of the second to sixth embodiments. 
     Eighth Embodiment 
       FIG. 24  is a perspective view for illustrating the outdoor heat exchanger  3  according to an eighth embodiment of the present invention. The outdoor heat exchanger  3  includes the heat exchanger main body  11  and a vortex generator  42 . The vortex generator  42  is arranged on a windward side of the plurality of heat exchange members  14  of the heat exchanger main body  11  in the x direction being the third direction, specifically, on the upstream side of the air stream A with respect to the plurality of heat exchange members  14 . A configuration of the heat exchanger main body  11  is the same as that of the first embodiment. The vortex generator  42  is known in the art, and is not independently relied upon for patentability. 
     The vortex generator  42  is configured to form the air stream A into a vortex flow. Further, the vortex generator  42  is arranged so as to be apart from the heat exchange main body  11  in the x direction being the third direction. A gap that is present between the vortex generator  42  and the heat exchange main body  11  is reduced to be as small as possible. The air stream A, which has passed through the vortex generator  42 , is formed into the vortex flow and passes between the plurality of heat exchange members  14 . In this manner, heat exchange between the refrigerant B flowing through the refrigerant flow passages  18  and the air stream A is promoted in a region from the ends of the heat exchange members  14  on the upstream side to the ends of the heat exchange members  14  on the downstream side. Other configurations are the same as those of the first embodiment. 
     In the outdoor heat exchanger  3  described above, the vortex generator  42  is arranged on the windward side of the heat exchange main body  11  in the x direction. Thus, the air stream. A, which has been formed into the vortex flow, can be supplied to the heat exchange main body  11 . In this manner, the heat exchange between the refrigerant B and the air stream A can be promoted in each of the heat exchange members  14 . Thus, the heat exchange performance of the outdoor heat exchanger  3  can be further improved. 
     Further, the vortex generator  42  is arranged at the position distant from the heat exchanger main body  11 . Thus, transfer of heat of the heat exchange members  14  to the vortex generator  42  can be prevented. As a result, generation of dew and frost on the vortex generator  42  can be prevented, and hence the air stream A in the vortex generator  42  can be prevented from being blocked by dew and frost. 
     In the example described above, the vortex generator  42  is arranged so as to be apart from the heat exchanger main body  11  in the x direction. However, the vortex generator  42  may be arranged so as to be held in contact with each of the heat exchange members  14  of the heat exchanger main body  11 . Even in this way, with the arrangement of the vortex generator  42  on the upstream side of the air stream A with respect to the heat generator main body  11 , the air stream A, which has been formed into the vortex flow, can be supplied to the heat generator main body  11 . Thus, the heat exchange performance in the heat exchanger main body  11  can be improved. 
     Further, in the example described above, the vortex generator  42  is applied to the outdoor heat exchanger  3  according to the first embodiment. However, the vortex generator  42  may be applied to the outdoor heat exchanger  3  according to the second to seventh embodiments. 
     Further, in the first to third embodiments and the fifth to eighth embodiments, the joining member  17  is used as a joining member configured to join the heat transfer plate  16  to the heat transfer pipe  15 . However, the joining member is not limited thereto. For example, an adhesive having heat conduction performance may be used as the joining member. 
     Further, in the first to third embodiments and the fifth to eighth embodiments, the heat transfer plate  16  is joined to the heat transfer pipe  15  through the joining member  17  therebetween. However, the heat transfer plate  16  may be directly joined to the heat transfer pipe  15  by, for example, welding or friction stir welding as in the second embodiment. 
     Further, in the first and third to eighth embodiments, the flat pipe having a flat sectional shape is used as the heat transfer pipe  15 . However, the circular pipe having a circular sectional shape may be used as the heat transfer pipe  15 . 
     Further, in the first to fifth, seventh, and eighth embodiments, the extending portions  162  and  163  project from the heat transfer plate main body portion  161  toward the upstream side and the downstream side of the air stream A, respectively. However, the extending portion  162  may project from the heat transfer plate main body portion  161  only toward the upstream side, which is one of the upstream side and the downstream side of the air stream A, or the extending portion  163  may project from the heat transfer plate main body portion  161  only toward the downstream side, which is one of the upstream side and the downstream side of the air stream A. 
     Further, in each of the embodiments described above, the present invention is applied to the outdoor heat exchanger  3 . However, the present invention may be applied to the indoor heat exchanger  5 . Further, in each of the embodiments described above, the refrigeration cycle apparatus according to the present invention is used as the air conditioning apparatus  1 . However, the use of the refrigeration cycle apparatus is not limited thereto. For example, the refrigeration cycle apparatus according to the present invention may be used as, for example, a cooling device, a refrigeration apparatus, or a water heater. Further, in each of the embodiments described above, the present invention is applied to the refrigeration cycle apparatus having the four-way valve  6 , which is capable of performing switching between the cooling operation and the heating operation. However, the present invention may be applied to a heat exchanger for a refrigeration cycle apparatus without the four-way valve  6 . 
     The present invention is not limited to the embodiments described above, and can be carried out with various changes within the scope of the present invention. Further, the present invention can also be carried out with combinations of the embodiments described above.