JPWO2013098872A1 - Outdoor unit, air conditioner, and outdoor unit manufacturing method - Google Patents

Abstract

The heat exchanger assembly 103 mounted on the outdoor unit 101 is configured to have opposing surfaces by forming notches without fin collars or notches having fin collars shorter than the stacking interval of the fins on the fins. At least a part of the stacking interval of the fins 2 is made larger than the stacking interval of the fins 2 constituting the surfaces other than the opposing surfaces.

Description

  The present invention relates to an outdoor unit and an air conditioner including the outdoor unit.

  Conventionally, commercial air conditioners used in buildings, factories, and the like include a relatively high-output model equipped with outdoor units that exhaust from the top two places in appearance. The structure of such an outdoor unit includes equipment such as a heat exchanger assembly, a compressor, and piping parts in the housing, and two propeller fans and two bell mouths that guide the air flow at the top of the housing. (For example, refer to Patent Document 1). In this outdoor unit, the outside air sucked into the housing by the action of the propeller fan is exchanged with the refrigerant when passing through the heat exchanger assembly, and is exhausted from the top of the housing by being guided by a bell mouth. Yes.

  A heat exchanger assembly mounted on such an outdoor unit generally has a two-row configuration of two heat exchangers. In this heat exchanger, a plurality of strip-shaped aluminum fins with circular holes are stacked and laminated, and a plurality of copper or aluminum transmissions having a circular cross section in a direction substantially perpendicular to the fins. After inserting the heat pipe, the inner diameter of the heat transfer pipe is expanded using a hydraulic or mechanical pipe expander to ensure the adhesion between the fins and the heat transfer pipe necessary for the heat transfer performance of the heat exchanger Many fin tube structures have been conventionally employed (for example, see Patent Document 2).

  The circular holes formed in the fins are subjected to burring to form a cylindrical collar at the edges in order to increase the contact area with the heat transfer tube, and the fin plate between the circular holes has ventilation A slit is provided to improve the heat exchange performance with. For the processing of round holes, collars and slits formed on the fins, a progressive die with multiple processes is placed on the press machine, and the press machine is continuously operated while supplying a strip-shaped aluminum hoop material. Thus, a technique that is sequentially performed is disclosed (see, for example, Patent Document 3).

  As a manufacturing method of a heat exchanger having a plate fin tube structure, a U-shaped forming part called a hairpin is formed by sequentially laminating a desired number of fins cut into a desired strip length after pressing, and then laminating a desired number of pieces. It is common to insert a plurality of long heat transfer tubes with a fin into a fin and expand the tube. As described above, since the lamination of the fins and the insertion of the heat transfer tubes are performed based on the collar, as a result, the fins are laminated and fixed at equal intervals of the collar height (for example, see Patent Document 4). ).

  In such a plate fin tube type heat exchanger, a plurality of heat transfer tubes are U-bends, distributors, etc., which are circular cross-section heat transfer tubes for pipe connection bent at the end in a U shape. By being connected to the parts by brazing, a continuous flow path of the refrigerant that folds back and forth in the laminated fin is formed.

  In addition, a heat exchanger having a plate fin tube structure configured by bending a laminated fin through which a heat transfer tube is inserted into an L shape over a plurality of times (for example, twice) is also disclosed (for example, patents). Reference 5). A heat exchanger having such a plate fin tube structure has a substantially U-shape in which laminated fins are bent over a plurality of times, and finally the fins are laminated and the internal heat transfer tubes are arranged in the contour direction. (See, for example, Patent Document 5). It should be noted that the heat exchangers formed by bending the laminated fins and having a substantially U-shape with three outer surfaces are in a state in which the fins are laminated at equal intervals of the fin collar height without being molded. ing.

  In addition, against the backdrop of the recent increase in energy problems, competition for energy saving and cost reduction is remarkable, and the shape and pitch of heat transfer tubes and fins (fin stacking interval, adjacent interval between heat transfer tubes) and materials (configuration of fins) Further improvement measures are being pursued with regard to materials and heat transfer tube components. Various measures such as changing the pitch of the fins according to the internal structure of the outdoor unit have been proposed (see, for example, Patent Documents 6 to 8).

JP 2008-138951 A (FIGS. 1-3, etc.) Japanese Examined Patent Publication No. 58-13249 (FIGS. 1 to 3 etc.) Japanese Patent Publication No. 58-9358 (FIGS. 1 to 5 etc.) Japanese Patent Publication No. 3-80571 (FIG. 1, FIG. 2, etc.) Patent No. 4417620 (FIG. 20 etc.) Japanese Unexamined Patent Publication No. 63-233296 (FIGS. 1 and 2 etc.) JP 2004245553 A (FIGS. 1 and 2 etc.) JP 2008-8541 A (FIG. 3 etc.)

  As described above, in the air conditioner adopting the structure and manufacturing method of superposition (lamination) of fins having round holes in the heat exchanger, circular tube insertion, and pipe expansion, the pitch between the fins is a burring process. The color height is fixed. Therefore, in the conventional air conditioner, it is difficult to change the pitch between the fins according to the internal structure of the outdoor unit in order to improve the performance.

  In particular, in an air conditioner in which a plurality of heat exchangers bent into a substantially U shape are arranged in parallel, the opening cross-sectional area into which air flows in the adjacent surfaces of the substantially U shape heat exchanger is The four surfaces (2 surfaces x 2 heat exchangers other than adjacent surfaces) are smaller than the sectional area of the opening through which air flows, and the wind speed is small. In order to improve the price-performance ratio in consideration of this, it is conceivable to change the stacking interval of the fins according to the position (arrangement position in the outdoor unit). It was practically difficult to change the pitch between the fins according to the structure.

  A structure in which the pitch between the fins is partially changed by dividing the heat exchanger or setting up the collar height has been proposed. In this case, it is necessary to provide a plurality of types of progressive fin molds or a mold having a mechanism capable of setting up the burring height in the mold. In addition, the complicated work of assembling the fin group is required. Therefore, the mold cost, press machine cost, and assembly cost become very expensive due to complicated and large molds and large press machines, which are difficult to realize. In addition, there is a problem with the restriction of the mold size that the number of types of color height is limited to 2 to 3 at the most, and it has been difficult to realize the color height.

  In order to avoid such a problem, a method in which the collar is set lower than the stacking interval of the fins and the fins are not overlapped on the basis of the color height is also conceivable. However, in this case, the heat transfer tubes cannot be inserted into the superposed fin group, and it is necessary to insert the fins one by one in the back by the length of the heat transfer tubes, which requires a lot of trouble. Will occur. In view of this point, it can be seen that changing the pitch of the fins is very difficult to realize.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide an air conditioner that can easily change the lamination pitch of fins.

  An outdoor unit according to the present invention includes a housing and at least two plate fin tube heat exchangers arranged in parallel in the housing and bent in an inner direction of the housing and having faces facing each other in the housing. An assembly and a fan that is disposed above the housing and exhausts air taken in from a side surface of the housing from an upper portion of the housing, and the heat exchanger assembly has no fin collar on the fin By forming a notch or a notch having a fin collar shorter than the stacking interval of the fins, at least a part of the stacking interval of the fins constituting the facing surface other than the facing surface It is made larger than the lamination | stacking space | interval of the fin of the part which comprises this surface.

  An air conditioner according to the present invention includes the outdoor unit described above and an indoor unit connected to the outdoor unit.

  According to the outdoor unit according to the present invention, fins can be distributed more effectively than in the past, heat exchange efficiency can be improved from the viewpoint of price-performance ratio, and energy saving and low cost can be realized. .

  According to the air conditioner according to the present invention, since the outdoor unit described above is provided, heat exchange efficiency can be improved and energy saving and low cost can be realized from the viewpoint of the price-performance ratio.

It is a schematic external view which shows an example of the external appearance structure of the outdoor unit which concerns on Embodiment 1 of this invention. It is a schematic perspective view for demonstrating the internal structure of the outdoor unit which concerns on Embodiment 1 of this invention. It is a schematic perspective view which shows roughly the structure of the heat exchanger assembly mounted in the outdoor unit which concerns on Embodiment 1 of this invention. It is a schematic perspective view which shows schematically the structure of the conventional heat exchanger assembly. It is a schematic perspective view which shows schematically a part of heat exchanger which comprises the heat exchanger assembly mounted in the outdoor unit which concerns on Embodiment 1 of this invention. It is a schematic perspective view which shows roughly the structure of the heat exchanger assembly mounted in the outdoor unit which concerns on Embodiment 2 of this invention. It is a circuit diagram which shows typically the basic composition of the air conditioner concerning Embodiment 3 of this invention. It is the schematic for demonstrating a part of manufacturing method of the heat exchanger assembly which concerns on Embodiment 4 of this invention. It is the schematic for demonstrating a part of manufacturing method of the heat exchanger assembly which concerns on Embodiment 4 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a schematic external view showing an example of an external configuration of an outdoor unit 101 according to Embodiment 1 of the present invention. Based on FIG. 1, the outline | summary of the external appearance structure of the outdoor unit 101 which concerns on Embodiment 1 of this invention is demonstrated. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  The outdoor unit 101 according to Embodiment 1 constitutes a part of an air conditioner that is used for business use, for example, in a building or factory. The outdoor unit 101 has an appearance as shown in FIG. 1 and is configured to exhaust air from two upper portions. The outdoor unit 101 constitutes an air conditioner by being connected to an indoor unit (not shown). Then, the refrigeration cycle is formed by pipe connection of the outdoor unit 101 and element devices (compressor, heat source side heat exchanger, expansion device, use side heat exchanger) mounted in the indoor unit, and the air conditioning target space ( For example, air conditioning of an indoor space in which an indoor unit is installed is executed. The air conditioner will be described in Embodiment 3.

  The outdoor unit 101 includes at least a housing 102, a heat exchanger assembly 103, a bell mouth 104, a cover 105, a compressor (not shown), and piping parts (not shown). In the outdoor unit 101, two fans (for example, a propeller fan or the like, which is the fan 55 described in Embodiment 3) are installed on the top of the housing 102. The air passing through the vessel assembly 103 is exhausted from the upper part of the housing 102. In FIG. 1, the bell mouth 104 is simplified and shown in a cylindrical shape.

  The housing 102 is configured in a substantially rectangular parallelepiped shape and constitutes the outer shell of the outdoor unit 101, and a part of the component devices constituting the refrigeration cycle is accommodated therein. The heat exchanger assembly 103 performs heat exchange between the air taken in by the fan and the refrigerant. Two heat exchanger assemblies 103 are provided corresponding to the number of fans installed. The bell mouth 104 guides air formed by a fan installed on the top of the housing 102. Two bell mouths 104 are provided corresponding to the number of fans installed.

  The cover 105 is provided on one of the four side surfaces of the housing 102 (for example, a surface on which a control board is installed and a worker performs maintenance work such as maintenance, a surface on the front side of the paper), and one surface of the housing 102. It covers. The remaining three surfaces of the casing 102 not covered with the cover 105 are exposed to the surroundings in most of the surfaces except for thin columnar or lattice members so that outside air can be sucked into the heat exchanger assembly 103. It is supposed to be. Note that FIG. 1 shows an example in which one cover 105 covers one surface of the housing 102, but the number of covers 105 is not particularly limited, and a plurality of covers 105 can cover the housing. One surface of 102 may be covered.

  FIG. 2 is a schematic perspective view for explaining the internal configuration of the outdoor unit 101. Based on FIG. 2, the outline | summary of the internal structure of the outdoor unit 101 is demonstrated. FIG. 2 schematically shows the internal structure of the outdoor unit 101 in which members other than the bottom plate 119 of the housing 102 and the component devices installed in the housing 102 are removed in order to show the air flow of the outdoor unit 101. It is shown schematically. Therefore, in FIG. 2, the bell mouth 104 appears to be separated from the housing 102. In addition, the white arrow shown in FIG. 2 represents the flow of the air formed by the effect | action of a fan. The size of the white arrow represents the wind speed.

  Below the two bell mouths 104, a heat exchanger assembly 103 that is bent into a substantially U shape so as to surround each of the two bell mouths 104 when the outdoor unit 101 is viewed from above is installed. The heat exchanger assembly 103 has a two-row configuration. The two heat exchanger assemblies 103 are arranged symmetrically with respect to a line connecting the centers of the casings 102 in the longitudinal direction. In the following description, the heat exchanger disposed outside the outdoor unit 101 in the two rows is referred to as the outer heat exchanger 106, and the heat exchanger disposed inside is referred to as the inner heat exchanger 107. And The adjacent surfaces of the two outer heat exchangers 106 are referred to as an outer adjacent surface 108, and the adjacent surfaces of the two inner heat exchangers 107 are referred to as an inner adjacent surface 109, respectively.

  The outer heat exchanger 106 and the inner heat exchanger 107 have, for example, a heat transfer tube having a flat cross-sectional shape (hereinafter referred to as a flat tube) having notch shapes with the same number and the same interval as the flat tubes in the plate long axis direction. Insertion holes are formed and inserted into plate-like fins arranged at a predetermined interval. The outer heat exchanger 106 and the inner heat exchanger 107 are, for example, circular heat transfer tubes having a circular cross section (hereinafter referred to as circular tubes) having the same number and the same interval as the circular tubes in the longitudinal direction of the plate surface. The insertion holes may be formed and inserted into plate-like fins arranged at a predetermined interval. The configurations of the outer heat exchanger 106 and the inner heat exchanger 107 will be described in detail with reference to FIG.

  Element devices such as a compressor installed in the housing 102 are provided on the bottom plate 119 of the housing 102 so that the heat exchanger assembly 103 is surrounded on three sides. The two heat exchanger assemblies 103 are composed of a pipe group that protrudes to an end face 125 of the heat exchanger assembly 103 (a surface facing the cover 105 of the outer adjacent surface 108 and the inner adjacent surface 109), and an occupied space (housing 102). In consideration of the internal occupation section of the heat exchanger assembly 103), they are arranged symmetrically in parallel with a gap 110 of a predetermined distance so as not to form an extra space in the housing 102.

  Therefore, when viewed as one housing 102 as shown in FIG. 1, two of the three surfaces of the two heat exchanger assemblies 103 excluding the adjacent surfaces (the outer adjacent surface 108 and the inner adjacent surface 109). The two heat exchanger assemblies 103 are arranged so that is positioned on three exposed surfaces of the housing 102. In FIG. 2, of the two surfaces excluding the adjacent surface of the heat exchanger assembly 103 on the left side of the sheet, the surface facing the adjacent surface is referred to as a surface 111, and the cover 105 and the surface facing the surface are illustrated as a surface 112. Similarly, in FIG. 2, of the two surfaces excluding the adjacent surface of the heat exchanger assembly 103 on the right side of the sheet, the surface facing the adjacent surface is referred to as a surface 114 and the surface facing the cover 105 is referred to as a surface 113. .

  However, since the heat exchanger assembly 103 is exposed to the periphery so that the outside air can be sucked into the heat exchanger assembly 103, the opposite surface of the housing 102 to the cover 105 is exposed to the outer adjacent surface 108 and the inner adjacent surface. Air is also taken in from the surface 109.

  The air flow in the outdoor unit 101 thus formed is approximately as shown in FIG. That is, air that has flowed into the housing 102 from the three surfaces of the housing 102 by the action of the fan passes through the heat exchanger assembly 103 and the bell mouth 104 and is then exhausted from the upper portion of the housing 102. At this time, in the surfaces 111 to 114 of the heat exchanger assembly 103, compared to the adjacent surface of the heat exchanger assembly 103, the opening cross-sectional area facing the outside of the housing 102 is large, so the ventilation resistance is small and the wind speed is higher. Air passes through. On the other hand, although air is also taken in from the outer adjacent surface 108 and the inner adjacent surface 109, since the opening cross-sectional area facing the outside of the housing 102 is small, the ventilation resistance is large and the air passes at a lower wind speed.

  FIG. 3 is a schematic perspective view schematically showing the structure of the heat exchanger assembly 103. FIG. 4 is a schematic perspective view schematically showing a structure of a conventional heat exchanger assembly (hereinafter referred to as a heat exchanger assembly 103 ′). Based on FIGS. 3 and 4, the structure of the heat exchanger assembly 103 will be described in comparison with the structure of the heat exchanger assembly 103 '. In addition, also about each member which comprises heat exchanger assembly 103 ', "'" is attached | subjected after a code | symbol for convenience, and each member which comprises heat exchanger assembly 103 mounted in the outdoor unit 101 which concerns on Embodiment 1 is attached. Comparison with members is easy.

  As described above, the heat exchanger assembly 103 is bent into a substantially U shape, and finally, a stack of fins and an internal heat transfer tube are arranged in the direction of the contour line 117. Further, the heat exchanger assembly 103 has a two-row configuration of an outer heat exchanger 106 and an inner heat exchanger 107. The two heat exchanger assemblies 103 are arranged so that the outer adjacent surfaces 108 of the two outer heat exchangers 106 and the inner adjacent surfaces 109 of the two inner heat exchangers 107 are opposed to each other.

  The outer heat exchanger 106 and the inner heat exchanger 107 constituting the heat exchanger assembly 103 have the same number of heat transfer tubes (flat tubes or circular tubes) as the heat transfer tubes in the longitudinal direction of the plate surface and the same interval between the heat transfer tubes. Insertion holes (including notches) with intervals are formed and inserted into plate-like fins arranged at predetermined intervals. After pressing, the fins are cut to the desired strip length, and are sequentially laminated in the collar part, and then a plurality of long heat transfer tubes each having a U-shaped part 115 called a hairpin are inserted. The

  The fins constituting the outer heat exchanger 106 and the inner heat exchanger 107 are stacked and fixed at a predetermined interval. That is, as shown in FIG. 3, the outer heat exchanger 106 and the inner heat exchanger 107 are configured by changing some fin intervals. Thereafter, a plurality of heat transfer tubes (flat tubes or circular tubes) are brazed to components such as a U-bend 116 for pipe connection and a distributor that are bent into a U shape at the end of the heat exchanger. Thereby, the continuous flow path of the refrigerant | coolant which folds several times in a fin is formed. Then, the laminated fins through which the heat transfer tubes are inserted are bent into an L shape over a plurality of times (for example, twice), and finally, the lamination of the fins and the internal heat transfer tubes are arranged in the direction of the contour line 117. A substantially U-shaped outer heat exchanger 106 and inner heat exchanger 107 are formed.

  Similarly, the heat exchanger assembly 103 'is also bent into a substantially U shape. Further, the heat exchanger assembly 103 'has a two-row configuration of an outer heat exchanger 106' and an inner heat exchanger 107 '. The two heat exchanger assemblies 103 ′ are arranged so that the outer adjacent surfaces 108 ′ of the two outer heat exchangers 106 ′ and the inner adjacent surfaces 109 ′ of the two inner heat exchangers 107 ′ face each other. Has been. Thus, in appearance, the heat exchanger assembly 103 and the heat exchanger assembly 103 'are the same.

  The outer heat exchanger 106 ′ and the inner heat exchanger 107 ′ constituting the heat exchanger assembly 103 ′ generally have the same number of circular tubes as the circular tubes in the plate major axis direction, and the interval between the circular tubes. Are inserted into plate-like fins arranged at regular intervals. As described in the background art, the circular hole of the fin is subjected to burring processing to form a cylindrical collar at the edge in order to increase the area in close contact with the circular tube, and the fin plate between the circular holes The part is provided with a slit for improving heat exchange performance with ventilation. The fins are cut into a desired strip length after press working, and after a desired number of layers are sequentially stacked in the collar portion, a plurality of long circular tubes having U-shaped forming portions 115 ′ called hairpins are formed. Inserted.

  As described above, in the outer heat exchanger 106 ′ and the inner heat exchanger 107 ′, the lamination of the fins and the circular tube insertion are performed on a color basis. As a result, the fins constituting the outer heat exchanger 106 'and the inner heat exchanger 107' are stacked and fixed at equal intervals in the collar height. That is, as shown in FIG. 4, the outer heat exchanger 106 ′ and the inner heat exchanger 107 ′ have a constant fin interval. Thereafter, the plurality of circular pipes are brazed with parts such as a U-bend 116 ′ for pipe connection and a distributor bent at the end of the heat exchanger into a U shape, so that a plurality of circular pipes are placed in the fins. In addition, a continuous flow path for the refrigerant is formed. Then, the laminated fin through which the circular tube is inserted is bent into an L shape a plurality of times (for example, twice), and finally the laminated fin and the internal heat transfer tube are arranged in the direction of the contour line 117 ′. The outer heat exchanger 106 ′ and the inner heat exchanger 107 ′ are substantially U-shaped.

  The pitch between the fins of the outer heat exchanger 106 ′ and the inner heat exchanger 107 ′ configured in this manner is fixed depending on the collar height of the burring process, and as described in the background art, It is difficult to change the fin pitch according to the internal structure.

  On the other hand, the outer heat exchanger 106 and the inner heat exchanger 107 constituting the heat exchanger assembly 103 have a structure in which the fin pitch can be easily changed unlike the conventional one. That is, unlike the conventional case, the outer heat exchanger 106 and the inner heat exchanger 107 constituting the heat exchanger assembly 103 have no fin collar, and the pitch between the fins is determined by the burring collar height. This is because the pitch of the fins can be easily changed because there is no gap or because a fin collar shorter than the stacking interval of the fins is provided. By facilitating the change of the fin pitch, the outdoor unit 101 according to the first embodiment can arrange the fins in consideration of the internal structure and from the viewpoint of the price to performance ratio. Thereby, in the outdoor unit 101 according to Embodiment 1, it is possible to further improve heat exchange efficiency and achieve energy saving.

  As shown in FIG. 2, the surfaces 111 to 114 of the heat exchanger assembly 103 face outside the housing 102 compared to the adjacent surfaces (the outer adjacent surface 108 and the inner adjacent surface 109) of the heat exchanger assembly 103. Since the opening cross-sectional area is large, the ventilation resistance is small, and air passes at a higher wind speed. That is, on the adjacent surface of the heat exchanger assembly 103, since the opening cross-sectional area facing the outside of the housing 102 is small, the ventilation resistance is large, and air passes at a low wind speed. Therefore, in the heat exchanger assembly 103, as shown in FIG. 3, the interval between the fins forming the outer adjacent surface 108 and the inner adjacent surface 109 is larger than the interval between the fins forming the surfaces 111 to 114. It is trying to become.

  FIG. 5 is a schematic perspective view schematically showing a part of the heat exchanger (the outer heat exchanger 106 and the inner heat exchanger 107) constituting the heat exchanger assembly 103. FIG. Based on FIG. 5, the structure of the outer side heat exchanger 106 and the inner side heat exchanger 107 is demonstrated in detail. 5A shows the outer heat exchanger 106 and the inner heat exchanger 107 provided with the flat tube 1, and FIG. 5B shows the outer heat exchanger 106 and the inner heat exchanger 107 provided with the circular tube 1A. Respectively. It should be noted that the outer heat exchanger 106 and the inner heat exchanger 107 provided with the flat tube 1 are collected together, and the flat tube heat exchanger 120 and the outer heat exchanger 106 and the inner heat exchanger 107 provided with the circular tube 1A are collected together. The circular pipe heat exchanger 120A will be referred to as a description.

  The outer heat exchanger 106 and the inner heat exchanger 107 shown in FIG. 5A have flat heat transfer tubes whose cross-sectional shapes are curved. That is, the flat tube heat exchanger 120 includes a plurality of flat tubes 1 having a flat cross section with a long side portion being a straight line and a short side portion having a curve such as a semicircular shape. The plurality of flat tubes 1 are arranged in parallel at a predetermined interval (for example, at equal intervals) in a direction orthogonal to the flow direction of the refrigerant flowing in the tubes.

  The flat tube heat exchanger 120 has a plurality of flat (rectangular) fins 2. The fins 2 are arranged in parallel with a predetermined interval in the refrigerant flow direction (direction orthogonal to the direction in which the flat tubes 1 are arranged). Since the fin 2 has a rectangular shape in which the long axis direction of the flat tube 1 is longer than the length of the flat tube 1 in the width direction (up and down direction in the drawing), the flat tube 1 is defined as the short direction. The major axis direction of 1 is defined as the longitudinal direction.

  A plurality of holes 3 are arranged in the flat tube 1 in the width direction. Inside the hole 3, for example, a refrigerant for exchanging heat with air passing through the flat tube heat exchanger 120 flows. The fin 2 is formed with a plurality of notches 4 in the longitudinal direction. In order to correspond to each flat tube 1, each notch 4 is formed, for example, with the same number and the same interval (except for both ends) as the flat tube 1. In addition, each notch 4 is formed to have a width dimension substantially the same as that of the flat tube 1. The notch 4 is formed so that one end of the fin 2 is opened. That is, the notches 4 are formed so as to be arranged in a comb-like shape in the longitudinal direction of the fins 2.

  Further, the fin 2 is formed with a gate-type (bridge-type) cut-and-raised portion 5 formed by cutting and raising a part of the fin 2 between the notches 4. This cut and raised 5 functions to promote heat exchange between air and the refrigerant. Further, a fin collar 6 raised in a direction perpendicular to the fin 2 is provided at the edge of each notch 4. The fin collar 6 has a shape cut and raised shorter than the stacking interval of the fins 2.

  Then, a plurality of flat tubes 1 are arranged in parallel, and the notches 4 of the fins 2 are inserted into the arranged flat tubes 1. Then, each flat tube 1 and each fin 2 are fixed by joining the flat tube 1 and the fin collar 6 with a brazing material or the like. With respect to such a flat tube heat exchanger 120, compared with a heat exchanger composed of a conventional circular tube and fins, it is equivalent or more in terms of expansion of the contact surface area between the refrigerant and the tube by narrowing the tube. It has been shown in many literatures that the volume to performance ratio can be obtained. In addition, the flat tube heat exchanger 120 having a size corresponding to the performance required for the outdoor unit 101 is selected and mounted on the outdoor unit 101.

  An outer heat exchanger 106 and an inner heat exchanger 107 shown in FIG. 5B have a circular tube 1A having a circular cross section. The plurality of circular pipes 1A are arranged in a staggered manner at a predetermined interval (for example, at equal intervals) in a direction orthogonal to the flow path direction of the refrigerant flowing in the pipe. The circular tube heat exchanger 120 </ b> A has flat plate-like fins 2 </ b> A similar to the fins 2 of the flat tube heat exchanger 120. The fins 2A are arranged in parallel with a predetermined interval in the flow direction of the refrigerant (a direction perpendicular to the direction in which the circular tubes 1A are arranged).

  In the circular pipe 1A, for example, a refrigerant for heat exchange with air passing through the circular pipe heat exchanger 120A flows. In addition, a plurality of notches 4A are formed in the fin 2A. In order to correspond to each circular pipe 1A, each notch 4A is formed, for example, at the same number as the circular pipe 1A and at the same interval (excluding both ends) as the arrangement interval of the circular pipes 1.

  The fin 2A is formed with a gate-type (bridge-type) cut-and-raised portion 5A in which a part of the fin 2A is cut and raised between the notches 4A. The cut and raised 5A functions to promote heat exchange between air and the refrigerant. Furthermore, a fin collar 6A raised in a direction perpendicular to the fin 2A is provided at the edge of each notch 4A. The fin collar 6 </ b> A has a shape that is cut and raised shorter than the stacking interval of the fins 2 </ b> A similarly to the fin collar 6.

  Then, a plurality of circular pipes 1A are arranged at a predetermined interval, and the notches 4A of the fins 2A are inserted into the arranged circular pipes 1A. Then, each circular pipe 1A and each fin 2A are fixed by joining the circular pipe 1A and the fin collar 6A with a brazing material or the like. The circular pipe heat exchanger 120 </ b> A having a size corresponding to the performance required for the outdoor unit 101 is selected and mounted on the outdoor unit 101.

  As described above, since the outdoor unit 101 includes the heat exchanger assembly 103 including the flat tube heat exchanger 120 or the circular tube heat exchanger 120A, the outdoor unit 101 has a larger fin pitch than the other surfaces 111 to 114. By stacking the fins to form the outer adjacent surface 108 and the inner adjacent surface 109, the fins can be distributed more effectively than in the past. Therefore, the outdoor unit 101 can arrange fin density suitable for performance improvement, can improve heat exchange efficiency from the viewpoint of price to performance ratio, and can achieve energy saving and low cost. In addition, in an outdoor unit with specifications that do not have any problem with the conventional performance, by reducing the total number of fins to the above-mentioned performance improvement, downsizing of the outdoor unit 101 while ensuring equivalent performance, Cost reduction is possible.

  Here, a case has been described in which a plurality of cut-and-raised portions 5 are formed between the notches 4 of the fin 2 so as to achieve an energy saving effect, but the cut-and-raised portions 5 are not necessarily provided. Similarly, here, a description has been given of an example in which a plurality of cut-and-raised portions 5A are formed between the cutouts 4A of the fin 2A so as to achieve a more energy-saving effect, but the cut-and-raised portions 5A are not necessarily provided. .

Embodiment 2. FIG.
FIG. 6 is a schematic perspective view schematically showing the structure of the heat exchanger assembly 103A mounted on the outdoor unit according to Embodiment 2 of the present invention. Based on FIG. 6, the structure of the heat exchanger assembly 103A will be described. The basic configuration of the outdoor unit according to Embodiment 2 is the same as that of outdoor unit 101 described in Embodiment 1. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

  The heat exchanger assembly 103A is bent and formed into a substantially U shape like the heat exchanger assembly 103 described in the first embodiment, and finally the fin stack and the internal heat transfer tube are arranged in the direction of the contour line 117. Has been. Further, the heat exchanger assembly 103A has a two-row configuration of an outer heat exchanger 106A and an inner heat exchanger 107A. The two heat exchanger assemblies 103A are arranged such that the outer adjacent surfaces 108A of the two outer heat exchangers 106A and the inner adjacent surfaces 109A of the two inner heat exchangers 107A face each other.

  The outer heat exchanger 106A and the inner heat exchanger 107A constituting the heat exchanger assembly 103A have heat transfer tubes (flat tubes or circular tubes) inserted in the same number and the same interval as the heat transfer tubes in the longitudinal direction of the plate surface. Are formed and inserted into plate-like fins arranged at predetermined intervals. After pressing, the fins are cut to the desired strip length, and are sequentially laminated in the collar part, and then a plurality of long heat transfer tubes each having a U-shaped part 115 called a hairpin are inserted. The

  The fins constituting the outer heat exchanger 106A and the inner heat exchanger 107A are stacked and fixed at a predetermined interval. Thereafter, a plurality of heat transfer tubes (flat tubes or circular tubes) are brazed to components such as a U-bend 116 for pipe connection and a distributor that are bent into a U shape at the end of the heat exchanger. Thereby, the continuous flow path of the refrigerant | coolant which folds several times in a fin is formed. Then, the laminated fins through which the heat transfer tubes are inserted are bent into an L shape over a plurality of times (for example, twice), and finally, the lamination of the fins and the internal heat transfer tubes are arranged in the direction of the contour line 117. A substantially U-shaped outer heat exchanger 106A and inner heat exchanger 107A are obtained.

  Unlike the conventional case, the outer heat exchanger 106A and the inner heat exchanger 107A constituting the heat exchanger assembly 103A have a structure in which the fin pitch can be easily changed. That is, since the outer heat exchanger 106A and the inner heat exchanger 107A constituting the heat exchanger assembly 103A are different from the conventional one, the pitch between the fins is not determined by the collar height of the burring process. Or in order to provide the fin collar shorter than the lamination | stacking space | interval of a fin, the change of a fin pitch is easy. The outer heat exchanger 106A and the inner heat exchanger 107A are configured with consideration given to the thickness of the fins and the stacking interval of the fins.

  Similar to the description in the first embodiment, the surfaces 111 to 114 of the heat exchanger assembly 103A are out of the casing as compared to the adjacent surfaces (the outer adjacent surface 108A and the inner adjacent surface 109A) of the heat exchanger assembly 103A. Since the opening cross-sectional area to face is large, ventilation resistance is small and air passes at a larger wind speed. That is, on the adjacent surface of the heat exchanger assembly 103A, the opening cross-sectional area facing the outside of the housing is small, so the ventilation resistance is large and air passes at a low wind speed.

  Therefore, in the heat exchanger assembly 103A, as shown in FIG. 6, a part of the interval between the fins constituting the outer adjacent surface 108A and the inner adjacent surface 109A is set as the interval between the fins forming the surfaces 111 to 114. To be bigger than. That is, the stacking interval of the fins on the surface 36 on the end portion side of the outer adjacent surface 108A is made larger than the stacking interval of the fins on the surface 38 on the R portion (curved portion) side. By doing in this way, the heat exchange efficiency in the part located in the part side among 108 A of outer side adjacent surfaces and the inner side adjacent surface 109A with a small opening cross-sectional area which faces outside a housing | casing can be improved.

  Since the outdoor unit according to the second embodiment is equipped with the heat exchanger assembly 103A in which the fin pitch can be easily changed similarly to the heat exchanger assembly 103 described in the first embodiment, the internal structure of the outdoor unit is Considering this further, fin density arrangement suitable for performance improvement is possible, and fins can be arranged based on the viewpoint of price to performance ratio. Thereby, in the outdoor unit according to Embodiment 2, it is possible to further improve the heat exchange efficiency and achieve more energy saving. In addition, in outdoor units with specifications that do not have any problem with conventional performance, the above-mentioned performance improvement is directed to the reduction of the total number of fins 2, thereby reducing the size of the outdoor unit while ensuring equivalent performance. Cost reduction is possible.

Embodiment 3 FIG.
FIG. 7 is a circuit diagram schematically showing a basic configuration of an air conditioner 50 according to Embodiment 3 of the present invention. Based on FIG. 7, the structure and operation | movement of the air conditioner 50 are demonstrated. The air conditioner 50 includes an outdoor unit and an indoor unit, and can perform a cooling operation or a heating operation by circulating a refrigerant through elemental devices mounted on the outdoor unit and the indoor unit. In the third embodiment, the air conditioner 50 is described as including the outdoor unit 101 according to the first embodiment. However, the air conditioner 50 may include the outdoor unit according to the second embodiment.

  The air conditioner 50 is mounted with a compressor 51, a heat source side heat exchanger 52, an expansion device 53, and a use side heat exchanger 54 as element devices connected by piping. Among these, the compressor 51 and the heat source side heat exchanger 52 are mounted on the outdoor unit 101, and the expansion device 53 and the use side heat exchanger 54 are mounted on the indoor unit 60. The expansion device 53 may be mounted not on the indoor unit 60 but on the outdoor unit 101. Although not shown, a flow path switching device such as a four-way valve for switching the refrigerant flow may be provided on the discharge side of the compressor 51.

  The compressor 51 sucks in the refrigerant and compresses the refrigerant to a high temperature / high pressure state, and is composed of, for example, an inverter compressor capable of capacity control. The heat source side heat exchanger 52 performs heat exchange between the air forcibly supplied from the fan 55 and the refrigerant. As the heat source side heat exchanger 52, the heat exchanger assembly described in the first embodiment or the second embodiment is applied. The expansion device 53 expands the refrigerant by depressurizing it, and is configured by a device whose opening degree can be variably controlled, for example, an electronic expansion valve. The use-side heat exchanger 54 performs heat exchange between air and a refrigerant that are forcibly supplied from a blower such as a fan (not shown). The number of fans 55 is the same as the number of heat exchanger assemblies constituting the heat source side heat exchanger 52, and supplies air to the heat source side heat exchanger 52.

An operation during heating operation and an operation during cooling operation of the air conditioner 50 will be briefly described.
[Heating operation]
When the compressor 51 is driven, the refrigerant is pressurized by the compressor 51 and discharged in a high temperature / high pressure state. The refrigerant discharged from the compressor 51 is supplied to the use-side heat exchanger 54, cooled by exchanging heat with air, and is in a low temperature / high pressure state. At this time, heating air is supplied from the indoor unit 60 to heat the air-conditioning target space. This refrigerant flows out of the use-side heat exchanger 54 and is expanded and depressurized by the expansion device 53 to be in a low temperature / low pressure state. The refrigerant returns to the compressor 51 again after being heated by the heat source side heat exchanger 52.

[Cooling operation]
When the compressor 51 is driven, the refrigerant is pressurized by the compressor 51 and discharged in a high temperature / high pressure state. The refrigerant discharged from the compressor 51 is supplied to the heat source side heat exchanger 52, cooled by exchanging heat with air, and is in a low temperature / high pressure state. This refrigerant flows out of the heat source side heat exchanger 52 and is expanded and depressurized by the expansion device 53 to be in a low temperature / low pressure state. This refrigerant is heated by the use side heat exchanger 54. At this time, air for cooling is supplied from the indoor unit 60 to cool the air-conditioning target space. The refrigerant that has flowed out of the use side heat exchanger 54 returns to the compressor 51 again.

  As described above, the air conditioner 50 includes the outdoor unit 101 on which the heat exchanger assembly 103 including the flat tube heat exchanger 120 or the circular tube heat exchanger 120A is mounted. By stacking the fins 2 with a larger fin pitch than the other surfaces 111 to 114 to form the outer adjacent surface 108 and the inner adjacent surface 109, the fins 2 can be distributed more effectively than in the prior art. . Therefore, the air conditioner 50 enables fin density arrangement suitable for performance improvement, can improve heat exchange efficiency from the viewpoint of price to performance ratio, and can achieve energy saving and low cost.

Embodiment 4 FIG.
FIG. 8 is a schematic diagram for explaining a part of the manufacturing method of the heat exchanger assembly according to Embodiment 4 of the present invention. Based on FIG. 8, the manufacturing method of the flat tube heat exchanger which comprises the heat exchanger assembly 103 is demonstrated. Here, the description will be made assuming that the flat tube heat exchanger 120 described in the first embodiment is manufactured. In the fourth embodiment, the same parts as those in the first to third embodiments are denoted by the same reference numerals and description thereof is omitted.

  First, a coil material wound with, for example, an aluminum thin plate to be the fin 2 is prepared. Then, the aluminum thin plate supplied from the coil material is pressed by a progressive die (not shown) mounted on a high-speed press. Then, the notch 4 is continuously press-molded on the aluminum thin plate together with the circular pilot holes 16 formed on both outer sides. At this time, an intermittent hoop feeding operation (arrow 17) is performed by utilizing a positioning pin inserted into the pilot hole 16, and the aluminum thin plate is fed out as a hoop-shaped fin train 18 as shown in FIG.

  The fin series 18 is separated as a single fin 2 by a cutter cutting operation (arrow 19) above the flat tubes 1 arranged in parallel. Thereafter, the fin 2 is gripped by a transfer mechanism (not shown) utilizing a cam and a servo, for example, and moves and rotates downward (arrow 20). By doing so, the fin 2 is inserted into the upper portion of the flat tube 1 from the opening side of the notch 4. Finally, the fin 2 is pushed in until a predetermined distance from the rear end of the fin group 21 already inserted in the flat tube 1 and the inner part of the notch 4 contact the upper portion of the flat tube 1. This completes the insertion and arrangement of the fins 2 into the flat tube 1.

  On the other hand, a plurality of flat tubes 1 are arranged in parallel, and can be moved and positioned in the long axis direction of the flat tubes 1 together. For example, a conveyance mechanism (not shown) including a servo, a ball screw, a linear guide, etc. , Hoop feed mechanism). And the flat tube 1 is positioned by the pitch feed operation | movement (arrow 22) of a conveyance mechanism in the major axis direction of the flat tube 1 so that it may become a desired space | interval with the tail of the fin group 21 already inserted.

  The cutting operation (arrow 19) and movement / rotation operation (arrow 20) of the fin 2 and the pitch feed operation (arrow 22) of the flat tube 1 are synchronized with the transfer mechanism and the servo mechanism, and the hoop feed of the high-speed press. Sequentially performed so as to follow the operation (arrow 17). As a result, the fins 2 are stacked at a predetermined interval. Note that the synchronization deviation between the high-speed press and the transfer mechanism can be absorbed by, for example, slacking the hoop material around the path roller, providing a material buffer, and increasing or decreasing the press stroke while detecting the amount of slack. Good.

  Further, the fin pitch can be adjusted to a desired interval by changing the pitch movement amount of the pitch feed operation (arrow 22). The pitch movement amount is adjusted by setting with the control controller of the transport mechanism. In the fin group (illustrated as the fin group 23 in FIG. 8) that constitutes the outer adjacent surface 108 and the inner adjacent surface 109 with a low wind speed, the pitch movement amount is set large, and the surfaces 111 to 114 are configured. For the fin group (shown as the fin group 24 in FIG. 8), the pitch movement amount is set small. Then, by laminating the required number of fins 2, a fin group assembly 25 composed of fin groups 23 having a large stacking interval and 24 having a small stacking interval is completed. In FIG. 8, the assembling of the fin group assembly 25 is shown.

  The fin group assembly 25 in which the lamination of the fins 2 is completed is performed by brazing or bonding in a furnace using a brazing material pre-coated on the flat tube 1 or an adhesive applied to a gap. It is fixed to the flat tube 1. After that, the fin group assembly 25 is connected to the piping parts in a state where the two rows are stacked, and is bent twice in the state where the two rows are stacked, so that the flat tube heat exchanger 120 having a substantially U shape is formed. Is completed (see FIG. 9).

  Since the flat tube heat exchanger 120 is manufactured by the manufacturing method as described above, when the stacking interval is changed, unlike the conventional operation of inserting the circular tube into the pre-stacked fin group, the color height is increased. It is possible to change to various fin pitches (fin stacking intervals) immediately by changing the controller command value of the pitch movement amount for the transport mechanism without the need for complicated molds or large presses to change the height. It becomes possible. That is, according to the manufacturing method according to the fourth embodiment, it is possible to easily change the stacking pitch of the fins 2 without increasing the die costs, the press machine costs, and the assembly work of the fins 2.

  Also, the flat tube heat exchanger 120 is different from the conventional one in which the collar is lowered and is not overlapped on the basis of the color, and it is not necessary to insert fins over the entire length of the heat transfer tube, regardless of the length of the flat tube 1, A desired number of fins 2 can be inserted into the flat tube 1. Therefore, the flat tube heat exchanger 120 easily realizes high-speed operation that follows the punching speed of a high-speed press of several hundred SPM (number of strokes per minute) with almost no influence of the workpiece shape. Fin pitch can be realized.

  FIG. 9 is a schematic diagram for explaining a part of the manufacturing method of the heat exchanger assembly according to Embodiment 4 of the present invention. Based on FIG. 9, a method for manufacturing the heat exchanger assembly 103 </ b> A described in the second embodiment will be described. In addition, in FIG. 9, the subsequent bending process of the flat tube heat exchanger 120 manufactured with the manufacturing method of FIG. 8 is illustrated.

  A heat exchanger bending apparatus 150 shown in FIG. 9 is for bending the fin group assembly 25 and includes at least an L bending jig 40 and a mounting table 41. The L bending jig 40 bends the flat tube 1 constituting the fin group assembly 25 substantially at a right angle (substantially L-shaped). In other words, the L-bending jig 40 includes a gripping portion 40a that grips the fin group assembly 25 and a movable portion 40b that rotationally drives the gripping portion 40a at a substantially right angle, and grips a predetermined position of the fin group assembly 25. The bent portion 40a is rotationally driven by the movable portion 40b, whereby the flat tube 1 is bent. At this time, the flat tube 1 is bent at a substantially right angle in the width direction.

  The mounting table 41 is for mounting the fin group assembly 25 that is slid in a predetermined direction (right side in FIG. 9) by a driving unit such as a roller (not shown). The mounting table 41 is provided with a guide rail (not shown), for example, and the fin group assembly 25 mounted on the mounting table 41 can be slid by being driven by the drive unit. ing.

  As shown in FIG. 8, the fin group assembly 25 in which the lamination of the fins 2 is completed is fixed to the flat tube 1. The fin group assembly 25 is stacked in two rows, and piping parts (for example, the U-shaped forming portion 115 and the U bend 116) are connected. In this state, the fin group assembly 25 is mounted on the mounting table 41 of the heat exchanger bending apparatus 150. The fin group assembly 25 mounted on the mounting table 41 is slid by the mounting table 41. When the fin group assembly 25 slides to a predetermined position (the position of the fin group 24 constituting the outer adjacent surface 108 and the inner adjacent surface 109), the fin group assembly 25 is gripped by the grip portion 40a of the L bending jig 40. Here, the gripping portion 40a grips the fin group 24 having a small stacking interval.

  The fin group assembly 25 gripped by the gripping portion 40a is bent at a substantially right angle by the gripping portion 40a that is rotationally driven by the action of the movable portion 40b while being slid (first L-shaped bending). Thus, the first R portion 44 is formed in the fin group assembly 25. When the first R portion 44 is formed, the grip portion 40 a releases the grip of the fin group assembly 25. Furthermore, the fin group assembly 25 is slid in the moving direction by the mounting table 41. Then, when the fin group assembly 25 slides to a predetermined position (the position of the fin group 24 constituting the surface 112 or the surface 113), it is gripped again by the gripping portion 40a of the L bending jig 40. Again, the gripping part 40a grips the fin group 24 with a small stacking interval.

  The fin group assembly 25 gripped by the gripping portion 40a is bent at a substantially right angle by the gripping portion 40a that is rotationally driven by the action of the movable portion 40b while being slid (second L-shaped bending). By doing so, the second R portion 45 is formed in the fin group assembly 25. When the second R portion 45 is formed, the grip portion 40 a releases the grip of the fin group assembly 25. As described above, the substantially U-shaped heat exchanger assembly 103A is completed.

  Thus, since the heat exchanger bending apparatus 150 holds the fin group 24 having a small stacking interval by the holding portion 40a, the stress applied to the end surface of the fin 2 when the flat tube 1 is bent can be reduced. Therefore, the heat exchanger bending apparatus 150 can efficiently suppress the occurrence of the fin 2 falling or buckling during bending. Therefore, even when the plate thickness of the fin 2 is thinner or the stacking interval of the fins 2 is wider, it is possible to arrange the fins 2 having a larger stacking interval while ensuring the work quality. Therefore, according to the method for manufacturing a heat exchanger assembly according to the fourth embodiment, a heat exchanger assembly that can improve heat exchange efficiency and achieve energy saving, low cost, and downsizing from the viewpoint of price-performance ratio is obtained. be able to.

  In the fourth embodiment, the method for manufacturing the heat exchanger assembly 103A described in the second embodiment has been described as an example. However, the method may be applied to the method for manufacturing the heat exchanger assembly 103 described in the first embodiment. Needless to say, it is good. However, in this case, attention should be paid to the portion gripped by the grip portion 40a.

  By the way, in each embodiment, the structure which the flat tube 1 located in an adjacent surface (the outer side adjacent surface 108, the inner side adjacent surface 109) is short compared with the length of the flat tube 1 located in surfaces other than an adjacent surface is an example. However, the present invention is not limited to this, and the length is the same as the length of the flat tube 1 located on the surface other than the adjacent surface, or longer than the length of the flat tube 1 located on the surface other than the adjacent surface. Needless to say, the same effect can be expected.

  Moreover, in each embodiment, although the example which has arrange | positioned two substantially U-shaped heat exchangers in parallel and mounted in the outdoor unit was shown, it is three or more if it is the arrangement structure provided with the adjacent surface. It goes without saying that the same effect can be expected even in an outdoor unit equipped with this heat exchanger. Further, in each embodiment, the number of upper and lower stages of the heat exchanger is not particularly described. However, as shown in each embodiment, the heat exchanger may have a single-stage configuration, or the heat exchanger may have two stages. It is good also as the above structure. Furthermore, in each embodiment, a heat exchanger having a two-row configuration is shown as an example. However, the present invention is not limited to this, and a heat exchanger having a single-row configuration or a heat exchanger having three or more rows may be used. A similar effect can be expected.

  1 flat tube, 1A circular tube, 2 fins, 2A fins, 3 holes, 4 cutouts, 4A cutouts, 5 cutouts, 5A cutouts, 6 fin collars, 6A fin collars, 16 pilot holes, 17 arrows, 18 fins 19 arrows, 20 arrows, 21 fin group, 22 arrows, 23 fin group, 24 fin group, 25 fin group assembly, 36 end face, 38 R face, 40 L bending jig, 40a Grasping part, 40b Movable part, 41 Mounting table, 44 1R part, 45 2R part, 50 Air conditioner, 51 Compressor, 52 Heat source side heat exchanger, 53 Expansion device, 54 Usage side heat exchanger, 55 Fan , 60 indoor unit, 101 outdoor unit, 102 housing, 103 heat exchanger assembly, 103A heat exchanger assembly, 104 bell mouth, 105 cover, 106 outer heat exchanger, 06A outer heat exchanger, 107 inner heat exchanger, 107A inner heat exchanger, 108 outer adjacent surface, 108A outer adjacent surface, 109 inner adjacent surface, 109A inner adjacent surface, 110 gap, 111 surface, 112 surface, 113 surface, 114 surface, 115 U-shaped forming part, 116 U bend, 117 contour line, 119 bottom plate, 120 flat tube heat exchanger, 120A circular tube heat exchanger, 125 end surface, 150 heat exchanger bending apparatus.

Claims (7)

A housing,
At least two plate fin tube type heat exchanger assemblies disposed in parallel within the housing, bent inwardly of the housing and having opposing surfaces in the housing;
A fan that is disposed above the housing and exhausts air taken in from a side surface of the housing from an upper portion of the housing;
The heat exchanger assembly is
By forming a notch without a fin collar on the fin or a notch having a fin collar shorter than the stacking interval of the fins,
At least a part of the stacking interval of the fins in the portion constituting the facing surface is made larger than the stacking interval of the fins in the portion configuring the surface other than the facing surface. Outdoor unit. The heat exchanger assembly is bent at a right angle at least once,
The stacking interval of the fins in the end portion side portion constituting the facing surface is made larger than the stacking interval of the fins in the bent portion side portion forming the facing surface. Item 1. The outdoor unit according to Item 1. The heat exchanger assembly is
The outdoor unit according to claim 2, wherein the outdoor unit is bent and formed along a remaining surface excluding one surface of the housing. The heat exchanger assembly is
A flat tube whose cross section is a flat shape with a long side as a straight line and a short side as a semicircular curve is configured to be inserted into the notch formed in the fin. The outdoor unit as described in any one of Claims 1-3. The fin is
The outdoor unit according to claim 4, wherein a plurality of bridge-like cuts are formed between the notches. The fin is
The outdoor unit according to 4 or 5, wherein the outdoor unit is fixed to the flat tube inserted into the notch by brazing or bonding. The outdoor unit according to any one of claims 1 to 6,
An air conditioner comprising: an indoor unit connected to the outdoor unit.

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