JP5849697B2 - Outdoor unit - Google Patents

Description

  The present invention relates to an outdoor unit.

  Conventionally, as disclosed in Patent Document 1 (Japanese Patent Application Laid-Open No. 2009-270748), in order to improve the refrigeration capacity, apart from the heat source side heat exchanger that performs heat exchange between the refrigerant and the air, An outdoor unit of a refrigeration apparatus provided with a liquid gas heat exchanger has been proposed. This liquid gas heat exchanger is a refrigerant heat exchanger that exchanges heat between refrigerants flowing inside.

  The refrigerant heat exchanger as described above is usually arranged on the downstream side of the air flow with respect to the heat source side heat exchanger. For this reason, during the cooling operation, the air heat-exchanged in the heat source side heat exchanger passes through the refrigerant heat exchanger, and the cooling efficiency in the refrigerant heat exchanger decreases. Further, the refrigerant heat exchanger is arranged on the downstream side of the air flow of the heat source side heat exchanger, so that the wind speed of the air that has passed through the heat source side heat exchanger is reduced, and heat exchange in the heat source side heat exchanger is performed. There is a concern that efficiency will also decrease.

  Therefore, an object of the present invention is to provide an outdoor unit that can suppress a decrease in cooling efficiency of a refrigerant-refrigerant heat exchanger and a decrease in heat exchange efficiency in a refrigerant-air heat exchanger.

  The outdoor unit according to the first aspect of the present invention is premised on an outdoor unit that blows air upward. The outdoor unit according to the first aspect of the present invention includes a casing, a refrigerant-air heat exchanger, and a refrigerant-refrigerant heat exchanger. The casing is formed with an air outlet for blowing out air at the top. The refrigerant-air heat exchanger is disposed in the casing and exchanges heat between the refrigerant flowing inside and the air. In the casing, an air flow path is formed that passes through the refrigerant-air heat exchanger and flows toward the outlet. In addition, a partition space that is partitioned from the air flow path by a partition member is formed in the casing and in the space above the refrigerant-air heat exchanger. The refrigerant-refrigerant heat exchanger is located in the partition space.

  In the present invention, since the refrigerant-refrigerant heat exchanger is located in the partition space partitioned from the air flow path, the air that has passed through the refrigerant-air heat exchanger hardly passes. Thereby, the fall of the cooling efficiency of a refrigerant | coolant-refrigerant heat exchanger can be suppressed. The refrigerant-refrigerant heat exchanger is located in a partition space located in the space above the refrigerant-air heat exchanger. Thereby, the fall of the wind speed of the air which passed the refrigerant | coolant-air heat exchanger can be suppressed, and the fall of the heat exchange efficiency in a refrigerant | coolant-air heat exchanger can be suppressed.

  The outdoor unit which concerns on the 2nd viewpoint of this invention is an outdoor unit which concerns on the 1st viewpoint of this invention, Comprising: The bell mouth arrange | positioned in the vicinity of a blower outlet in a casing is further provided. The bell mouth is a partition member having a first partition portion and a second partition portion. The first partition section partitions the refrigerant-air heat exchanger and the refrigerant-refrigerant heat exchanger in the vertical direction. The second partition portion extends upward from the first partition portion.

  In the present invention, since the air channel and the refrigerant-refrigerant heat exchanger can be partitioned by the bell mouth, it is possible to suppress a decrease in the cooling efficiency of the refrigerant-refrigerant heat exchanger.

  An outdoor unit according to a third aspect of the present invention is an outdoor unit according to the first or second aspect of the present invention, wherein the refrigerant-air heat exchanger includes a first header extending in the vertical direction, a first heat The refrigerant-refrigerant heat exchanger includes a second header extending in the vertical direction and a second heat exchange part. The first heat exchanging portion extends in a direction intersecting the first header, and is disposed between each of the plurality of first flat tubes whose end portions are connected to the first header and the plurality of first flat tubes. 1 heat transfer fin. The second heat exchanging portion extends in a direction intersecting the second header, and is disposed between each of the plurality of second flat tubes whose end portions are connected to the second header and the plurality of second flat tubes. 2 heat transfer fins. The first header and the second header are integrated.

  In the present invention, by integrating the first header and the second header, the refrigerant-air heat exchanger and the refrigerant-refrigerant heat exchanger can be integrated and made compact. Thereby, the occupied volume in the casing of the refrigerant-air heat exchanger and the refrigerant-refrigerant heat exchanger can be reduced.

  The outdoor unit according to the fourth aspect of the present invention is an outdoor unit according to the third aspect of the present invention, and a gap is secured between the first heat exchange part and the second heat exchange part, A heat insulating material is disposed in the gap.

  In this invention, the heat exchange between a 1st heat exchange part and a 2nd heat exchange part can be suppressed. Therefore, it is possible to suppress a decrease in heat exchange efficiency in each of the refrigerant-air heat exchanger and the refrigerant-refrigerant heat exchanger.

  In the outdoor unit according to the first aspect of the present invention, it is possible to suppress a decrease in cooling efficiency of the refrigerant-refrigerant heat exchanger and a decrease in heat exchange efficiency in the refrigerant-air heat exchanger.

  In the outdoor unit according to the second aspect of the present invention, a decrease in the cooling efficiency of the refrigerant-refrigerant heat exchanger can be suppressed.

  In the outdoor unit according to the third aspect of the present invention, the volume occupied in the casing of the refrigerant-air heat exchanger and the refrigerant-refrigerant heat exchanger can be reduced.

  In the outdoor unit according to the fourth aspect of the present invention, it is possible to suppress a decrease in heat exchange efficiency in each of the refrigerant-air heat exchanger and the refrigerant-refrigerant heat exchanger.

The schematic block diagram of the air conditioning apparatus as an example of the freezing apparatus which has the outdoor unit which concerns on this invention. The schematic front view of a refrigerant | coolant-air heat exchanger and a refrigerant | coolant-refrigerant heat exchanger. The outline external view of an outdoor unit. The perspective view of the outdoor unit of the state which removed a part of casing and the fan. The schematic diagram in a casing. The schematic diagram which shows the arrangement | positioning relationship between the conventional refrigerant | coolant-air heat exchanger and a refrigerant | coolant-refrigerant heat exchanger.

  Hereinafter, embodiments of an outdoor unit according to the present invention will be described with reference to the drawings. In addition, embodiment of the heat exchanger which concerns on this invention is one of the specific examples of this invention, Comprising: The technical scope of this invention is not limited.

(1) Configuration of Air Conditioner 1 FIG. 1 is a refrigerant circuit diagram of an air conditioner 1 as an example of a refrigeration apparatus having an outdoor unit 20 according to the present invention. FIG. 2 is a schematic front view of the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5. FIG. 3 is a schematic external view of the outdoor unit 20. FIG. 4 is a perspective view of the outdoor unit 20 in a state where a part of the casing 20a and the fan 29 are removed. FIG. 5 is a schematic view inside the casing 20a. In addition, the front of the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5 in FIG. 2 refers to a portion on the upstream side in the air flow direction. 4, the illustration of the compression mechanism 2 and the like is omitted, and the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5 are shown in a simplified manner.

  The air conditioner 1 is a multi-type air conditioner for buildings, and has a configuration in which a plurality of indoor units 30a and 30b are connected in parallel to one outdoor unit 20, as shown in FIG. doing. The air conditioner 1 can switch between a cooling operation and a heating operation, and performs a refrigeration cycle using a refrigerant that operates in a supercritical region such as carbon dioxide.

  The refrigerant circuit 10 of the air conditioner 1 mainly includes a compression mechanism 2, a switching mechanism 3, a refrigerant-air heat exchanger 4, a refrigerant-refrigerant heat exchanger 5, expansion mechanisms 6a and 6b, and use side heat. Exchangers 7a and 7b and a receiver 9 are provided. The compression mechanism 2, the switching mechanism 3, the refrigerant-air heat exchanger 4, the refrigerant-refrigerant heat exchanger 5, and the receiver 9 are accommodated in a casing 20a of the outdoor unit 20 (see FIG. 3 and FIG. 4). The expansion mechanisms 6a and 6b and the use side heat exchangers 7a and 7b are accommodated in casings (not shown) of the indoor units 30a and 30b. Hereinafter, each component which comprises the refrigerant circuit 10 is demonstrated.

(2) Components of refrigerant circuit 10 (2-1) Compression mechanism 2
The compression mechanism 2 has a sealed structure in which a compression element drive motor 21b, a drive shaft 21c, a first compression element 2c, and a second compression element 2d are accommodated in a compression mechanism casing 21a. The compression element drive motor 21b drives the first compression element 2c and the second compression element 2d via the drive shaft 21c. The compression mechanism 2 sucks low-pressure refrigerant from the suction pipe 2a and discharges the sucked low-pressure refrigerant to the intermediate refrigerant pipe 8 after being compressed by the first compression element 2c. Further, the compression mechanism 2 sucks the refrigerant discharged to the intermediate refrigerant pipe 8 into the second compression element 2d and further compresses it, and then discharges it to the discharge pipe 2b. Here, the intermediate refrigerant pipe 8 is a refrigerant pipe for allowing the refrigerant compressed and discharged by the first compression element 2c to flow into the heat source side heat exchanging section 40 and then sucked into the second compression element 2d. . In the following description, of the intermediate refrigerant pipe 8, the refrigerant pipe connecting the first compression element 2c and the heat source side heat exchange unit 40 (described later) of the refrigerant-air heat exchanger 4 is referred to as the first intermediate refrigerant. A refrigerant pipe indicated as a pipe 8a and connecting the second compression element 2d and the heat source side heat exchanging section 40 will be indicated as a second intermediate refrigerant pipe 8b. The discharge pipe 2 b is a refrigerant pipe for sending the refrigerant discharged from the compression mechanism 2 to an intermediate heat exchange unit 60 (described later) of the refrigerant-air heat exchanger 4.

(2-2) Switching mechanism 3
The switching mechanism 3 is a mechanism for switching the flow direction of the refrigerant in the refrigerant circuit 10. The switching mechanism 3 is a four-way switching valve connected to the suction side of the compression mechanism 2, the discharge side of the compression mechanism 2, the heat source side heat exchanger 40 of the refrigerant-air heat exchanger 4 and the use side heat exchangers 7a and 7b. It is. During the cooling operation, the switching mechanism 3 connects the discharge side of the compression mechanism 2 and one end of the heat source side heat exchange unit 40 and connects the suction side of the compression mechanism 2 and one end of the use side heat exchangers 7a and 7b. (Refer to the solid line of the switching mechanism 3 in FIG. 1). On the other hand, during the heating operation, the switching mechanism 3 connects the discharge side of the compression mechanism 2 and one end of the use side heat exchangers 7a and 7b, and connects the suction side of the compression mechanism 2 and one end of the heat source side heat exchange unit 40. Connect (see dotted line of switching mechanism 3 in FIG. 1).

(2-3) Refrigerant-air heat exchanger 4
The refrigerant-air heat exchanger 4 exchanges heat between the refrigerant flowing inside and the air passing outside. The air passing outside the refrigerant-air heat exchanger 4 is supplied by the fan 29 and flows from the front side to the back side in FIG. The fan 29 is driven by a fan drive motor 29a. The refrigerant-air heat exchanger 4 includes a heat source side heat exchange unit 40 and an intermediate heat exchange unit 60. The heat source side heat exchanging unit 40 and the intermediate heat exchanging unit 60 have a two-stage structure in which the heat source side heat exchanging unit 40 is arranged on the upper stage and the intermediate heat exchanging unit 60 is arranged on the lower stage. The heat source side heat exchanging unit 40 and the intermediate heat exchanging unit 60 are connected by brazing one end of each of headers 43a and 43b and headers 63a and 63b (corresponding to the first header) to be described later. It is integrated as a whole. The header in which the headers 43 a and 43 b and the headers 63 a and 63 b are integrated constitutes the first header of the refrigerant-air heat exchanger 4.

(2-3-1) Heat source side heat exchange unit 40
The heat source side heat exchanging unit 40 functions as a radiator of the refrigerant compressed by the compression mechanism 2 during the cooling operation, and is a refrigerant compressed by the compression mechanism 2 and radiated by the use side heat exchangers 7a and 7b during the heating operation. Functions as a heater. One end of the heat source side heat exchange unit 40 is connected to the switching mechanism 3, and the other end is connected to the economizer heat exchange unit 70.

  The heat source side heat exchange part 40 mainly has a first part 41 and a second part 42 arranged in a row in the air flow direction. The first part 41 and the second part 42 have the same configuration. The first part 41 is located upstream in the air flow direction, and the second part 42 is located downstream in the air flow direction. Here, since FIG. 2 is a front view, only the first part 41 located upstream in the air flow direction is shown, but the component numbers of the second part 42 hidden by the first part 41 are shown. Will also be shown in parentheses.

  The first part 41 and the second part 42 are each mainly composed of a pair of headers 43a, 43b extending in the vertical direction apart from each other and a direction between the pair of headers 43a, 43b extending in the headers 43a, 43b. Arranged between each of the plurality of flat tubes 44a, 44b extending in the intersecting direction (specifically, the horizontal direction) and having longitudinal ends connected to the headers 43a, 43b and the plurality of flat tubes 44a, 44b. It is a laminated heat exchange section composed of heat transfer fins 45a and 45b. The plurality of flat tubes 44a and 44b are arranged at predetermined intervals in the vertical direction. Here, the refrigerant discharged from the compression mechanism 2 flows into one of the pair of headers 43b and 43b of the second portion 42 (in this embodiment, the header 43b on the left side of FIG. 2). An opening (not shown) serving as an entrance is formed, and one of the pair of headers 43a and 43a of the first portion 41 (in this embodiment, the header 43a on the left side of FIG. 2) An opening (not shown) is formed as an outlet through which the refrigerant flows out from the heat source side heat exchanging section 40 to a first economizer refrigerant pipe 71b described later.

  In addition, the 1st part 41 and the 2nd part 42 can distribute | circulate a refrigerant | coolant between one header (this embodiment header 43a, 43b of the paper surface right side of FIG. 2) among two headers 43a, 43b. It is comprised so that it may become.

  In the heat source side heat exchanging unit 40 of the present embodiment, the refrigerant that has flowed into the header 43b on the left side in FIG. 2 of the second part 42 passes through the flat tube 44b and the header 43b on the right side in FIG. Flow into. Then, the refrigerant flows from the header 43b on the right side of FIG. 2 of the second part 42 to the header 43a on the right side of FIG. 2 of the first part 41, and flows through the flat tube 44a to the left side of FIG. The header 43a flows to the first economizer refrigerant pipe in a sampling manner. In order to allow the refrigerant to flow between the headers 43a and 43b, another member may be used.

(2-3-2) Intermediate heat exchange unit 60
The intermediate heat exchange unit 60 is a heat exchange unit that is disposed below the heat source side heat exchange unit 40 and integrated with the heat source side heat exchange unit 40. The intermediate heat exchange unit 60 is provided in the intermediate refrigerant pipe 8, and is configured such that one end thereof is connected to the first compression element 2c and the other end is connected to the second compression element 2d. ing. The intermediate heat exchanging unit 60 functions as a refrigerant for intermediate-pressure refrigerant in the refrigeration cycle that is compressed by the first compression element 2c and sucked into the second compression element 2d during the cooling operation.

  The intermediate heat exchange part 60 mainly has a third part 61 and a fourth part 62 arranged in a row in the air flow direction. The third part 61 and the fourth part 62 have the same configuration. The third part 61 is located on the upstream side in the air flow direction, and the fourth part 62 is located on the downstream side in the air flow direction. Since FIG. 2 is a front view, only the third part 61 located upstream in the air flow direction is shown, but the numbers of the components of the fourth part 62 hidden by the third part 61 are shown. Are also shown in parentheses.

  Each of the third part 61 and the fourth part 62 is mainly composed of a pair of headers 63a and 63b extending in the vertical direction apart from each other, and a direction between the pair of headers 63a and 63b extending in the headers 63a and 63b. Arranged between each of the plurality of flat tubes 64a and 64b extending in the intersecting direction (specifically, the horizontal direction) and having longitudinal ends connected to the headers 63a and 63b and the plurality of flat tubes 64a and 64b. It is a laminated heat exchanging part composed of heat transfer fins 65a and 65b. The plurality of flat tubes 64a and 64b are arranged at predetermined intervals in the vertical direction.

  In the intermediate heat exchange section 60 of the present embodiment, the refrigerant that has flowed through the first intermediate refrigerant pipe 8a flows into the headers 63a and 63b on the left side of FIG. 2 and passes through the flat pipes 64a and 64b in FIG. It flows to the headers 63a and 63b on the right side of the page. Then, it flows out to the second intermediate refrigerant pipe 8b.

  The third part 61 and the first part 41 have substantially the same planar view position, and the fourth part 62 and the second part 42 have substantially the same planar view position.

  As described above, the flat tubes 44 a and 44 b of the heat source side heat exchanging unit 40 and the flat tubes 64 a and 64 b of the intermediate heat exchanging unit 60 constitute the first flat tube of the refrigerant-air heat exchanger 4. It will be. Further, the heat transfer fins 45 a and 45 b of the heat source side heat exchange unit 40 and the heat transfer fins 65 a and 65 b of the intermediate heat exchange unit 60 constitute a first heat transfer fin of the refrigerant-air heat exchanger 4. Become. The flat tubes 44a and 44b and the heat transfer fins 45a and 45b of the heat source side heat exchange unit 40 and the flat tubes 64a and 64b and the heat transfer fins 65a and 65b of the intermediate heat exchange unit 60 are refrigerant-air heat exchangers. 4 1st heat exchange parts are constituted.

(2-4) Refrigerant-refrigerant heat exchanger 5
The refrigerant-refrigerant heat exchanger 5 is a heat exchanger that exchanges heat between refrigerants, and is disposed in the space above the refrigerant-air heat exchanger 4. The refrigerant-refrigerant heat exchanger 5 includes an economizer heat exchanging unit 70 and a supercooling heat exchanging unit 80. The economizer heat exchanging unit 70 and the supercooling heat exchanging unit 80 are arranged side by side in a row in the air flow direction. Specifically, the supercooling heat exchanging unit 80 is located upstream of the economizer heat exchanging unit 70 in the air flow direction, and the economizer heat exchanging unit 70 is airflowed with respect to the subcooling heat exchanging unit 80. It is located downstream in the direction. The refrigerant-refrigerant heat exchanger 5 is integrated with the refrigerant-air heat exchanger 4. Specifically, the first header of the refrigerant-air heat exchanger 4 and the second header (described later) of the refrigerant-refrigerant heat exchanger 5 are connected to each other in the longitudinal direction by brazing. Thus, the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5 are integrated.

(2-4-1) Economizer heat exchanger 70
The economizer heat exchanging unit 70 is a heat exchanging unit arranged between the heat source side heat exchanging unit 40 and the use side heat exchangers 7a and 7b in the refrigerant circuit 10, and includes the first economizer refrigerant flow channel 71a and the first heat exchanging unit 71a. 2 economizer refrigerant flow paths 72a are formed. The first economizer refrigerant flow path 71a and the second economizer refrigerant flow path 72a are configured such that the refrigerants flowing through them respectively oppose each other. In the economizer heat exchanging unit 70, heat exchange is performed between the refrigerant flowing through the first economizer refrigerant flow path 71a and the refrigerant flowing through the second economizer refrigerant flow path 72a during the cooling operation. In addition, the 1st economizer refrigerant | coolant flow path 71a is formed of the several hole (not shown) formed in the flat tube 76aa mentioned later. The second economizer refrigerant flow path 72a is formed by a plurality of holes (not shown) formed in a flat tube 76ab described later.

  The refrigerant cooled in the heat source side heat exchanging unit 40 flows through the first economizer refrigerant flow path 71a during the cooling operation. The second economizer refrigerant flow path 72a is a part of the refrigerant branched from the refrigerant cooled in the heat source side heat exchanging unit 40 during the cooling operation, and is reduced to near the intermediate pressure by the economizer inlet expansion mechanism 79. The refrigerant is flowing. Here, the refrigerant pipe connecting the heat source side heat exchange section 40 and the flat pipe 76aa forming the first economizer refrigerant flow path 71a of the economizer heat exchange section 70 is referred to as a first economizer refrigerant pipe 71b, and the economizer heat exchange section 70. A refrigerant pipe connecting the flat pipe 76aa and the receiver 9 is a second economizer refrigerant pipe 71c. An economizer branch pipe 72 is connected to the first economizer refrigerant pipe 71b.

  The economizer branch pipe 72 is a refrigerant pipe capable of branching a part of the refrigerant cooled by the heat source side heat exchange unit 40 and flowing it to the economizer heat exchange unit 70 and then returning it to the second compression element 2d. The flat tube 76ab forming the second economizer refrigerant flow path 72a constitutes the economizer branch pipe 72. The economizer branch pipe 72 includes a first economizer branch pipe 72b and a second economizer branch pipe 72c in addition to the flat pipe 76ab. Here, the first economizer branch pipe 72b is a refrigerant pipe connecting the first economizer refrigerant pipe 71b and the flat pipe 76ab. The second economizer branch pipe 72c is a refrigerant pipe that connects the flat pipe 76ab and the second intermediate refrigerant pipe 8b. An economizer inlet expansion mechanism 79 is provided in the first economizer branch pipe 72b. The economizer inlet expansion mechanism 79 is a depressurization mechanism that depressurizes the high-pressure refrigerant cooled by the heat source side heat exchange unit 40 to near the intermediate pressure. The economizer inlet expansion mechanism 79 uses an electric expansion valve capable of adjusting the opening. The economizer inlet expansion mechanism 79 is adjusted in opening during the cooling operation and is controlled to be closed during the heating operation.

  Hereinafter, the detailed configuration of the economizer heat exchange unit 70 will be described with reference to FIG. 2 is a front view, the economizer heat exchanging portion 70 located downstream in the air flow direction in the refrigerant-refrigerant heat exchanger 5 is hidden by the supercooling heat exchanging portion 80, but the economizer heat exchanging portion The number of the component 70 is also shown in parentheses.

  The economizer heat exchanging section 70 mainly has a plurality of (two in this embodiment) stacked heat exchanging sections 73 arranged in a row in the air flow direction.

  The plurality of stacked heat exchanging units 73 mainly include a pair of headers 75a extending in the vertical direction spaced apart from each other, and a direction intersecting the direction in which the header 75a extends between the pair of headers 75a (specifically, A plurality of (in this embodiment, two) flat tube units 76a extending in the horizontal direction) and having end portions in the longitudinal direction connected to the header 75a, and heat transfer fins 77a disposed between the plurality of flat tube units 76a. Consists of The plurality of flat tube units 76a are arranged at predetermined intervals in the vertical direction. The flat tube unit 76a has a flat tube 76aa and a flat tube 76ab arranged in the vertical direction. The flat tube 76aa and the flat tube 76ab have the same configuration. The flat tubes 76aa and 76ab are arranged such that the normal lines of the flat surfaces extend in the vertical direction. Further, the flat tube unit 76a is configured so that the two flat tubes 76aa and 76ab are in close contact with each other. As described above, the flat tubes 76aa and 76ab are each formed with a plurality of holes (not shown). The plurality of holes are formed so that the refrigerant flowing through each of the holes flows in parallel.

(2-4-2) Supercooling heat exchanger 80
The subcooling heat exchange unit 80 includes a first subcooling refrigerant channel 81a and a second subcooling refrigerant channel 81b, and a refrigerant flowing through the first subcooling refrigerant channel 81a during cooling operation, This is a heat exchanging section that exchanges heat with the refrigerant flowing through the second subcooling refrigerant flow path 81b. In the supercooling heat exchanger 80, the refrigerant flowing to the use side heat exchangers 7a and 7b is in a supercooled state during the cooling operation. The first subcooling refrigerant flow path 81a and the second subcooling refrigerant flow path 81b are configured such that the refrigerants flowing through them respectively face each other. The first supercooling refrigerant channel 81a is formed by a plurality of holes (not shown) formed in a flat tube 86aa described later. The second supercooling refrigerant channel 81b is formed by a plurality of holes (not shown) formed in a flat tube 86ab described later.

  The high-pressure refrigerant extracted from the receiver 9 flows through the first subcooling refrigerant channel 81a. The refrigerant that is branched from the receiver connecting pipe 94 and has been decompressed to a low pressure by a suction expansion mechanism 96 described later flows through the second subcooling refrigerant flow path 81b.

  Here, the receiver connecting pipe 94 is a refrigerant pipe having one end connected to the receiver 9 and the other end connected to the flat pipe 86aa that forms the first subcooling refrigerant flow path 81a of the subcooling heat exchange section 80. . The flat tube 86ab forming the second subcooling refrigerant flow path 81b of the subcooling heat exchange unit 80 constitutes a suction return pipe 95 connected to the receiver connecting pipe 94. The suction return pipe 95 is a refrigerant pipe that can extract the refrigerant from the receiver 9 and return it to the suction pipe 2a via the supercooling heat exchange section 80. One end of the suction return pipe 95 is connected to the receiver connection pipe 94. The end is connected to the suction pipe 2a. A suction expansion mechanism 96 for reducing the refrigerant extracted from the receiver 9 to a low pressure is provided at a position upstream of the refrigerant flow of the supercooling heat exchanger 80 in the suction return pipe 95. The suction expansion mechanism 96 uses an electric expansion valve whose opening degree can be adjusted. The suction expansion mechanism 96 is adjusted in opening degree during the cooling operation, and is controlled to be closed during the heating operation. The refrigerant that has exited the flat tube 86aa of the supercooling heat exchange unit 80 is sent to the expansion mechanisms 6a and 6b through the refrigerant tube 5a. Here, the refrigerant pipe 5a is a refrigerant pipe having one end connected to the flat pipe 86aa of the supercooling heat exchange unit 80 and the other end connected to the expansion mechanisms 6a and 6b.

  Hereinafter, the detailed structure of the supercooling heat exchange part 80 is demonstrated using FIG.

  The supercooling heat exchanging unit 80 mainly includes a plurality of (two in this embodiment) stacked heat exchanging units 83 arranged in a row in the air flow direction.

  The plurality of stacked heat exchange units 83 are mainly composed of a pair of headers 85a extending in the vertical direction apart from each other and a direction intersecting the direction in which the header 85a extends between the pair of headers 85a (specifically, A plurality (two in this embodiment) of flat tube units 86a extending in the horizontal direction) and having end portions in the longitudinal direction connected to the header 85a, and heat transfer fins 87a disposed between the plurality of flat tube units 86a. It is the heat exchange part comprised from these. The plurality of flat tube units 86a are arranged at predetermined intervals in the vertical direction. The flat tube unit 86a has a flat tube 86aa and a flat tube 86ab arranged in the vertical direction. The flat tube 86aa and the flat tube 86ab have the same configuration. The flat tubes 86aa and 86ab are arranged such that the normal lines of the flat surfaces extend in the vertical direction. Further, the flat tube unit 86a is configured so that the two flat tubes 86aa and 86ab are in close contact with each other. Although not shown in the drawings, the flat tubes 86aa and 86ab are each formed with a plurality of holes, and the plurality of holes are formed so that the refrigerant flowing through each of them flows in parallel.

  As described above, the flat tubes 76aa and 76ab of the economizer heat exchanging unit 70 and the flat tubes 86aa and 86ab of the supercooling heat exchanging unit 80 constitute the second flat tube of the refrigerant-refrigerant heat exchanger 5. Will be. Further, the heat transfer fins 77 a of the economizer heat exchanging unit 70 and the heat transfer fins 87 a of the supercooling heat exchanging unit 80 constitute the second heat transfer fins of the refrigerant-refrigerant heat exchanger 5. The flat tubes 76aa and 76ab and the heat transfer fins 77a of the economizer heat exchanging unit 70 and the flat tubes 86aa and 86ab and the heat transfer fins 87a of the supercooling heat exchanging unit 80 are the second of the refrigerant-refrigerant heat exchanger 5. This constitutes the heat exchange unit.

  Here, the flat tube unit 76a located at the bottom of the economizer heat exchanging unit 70, the flat tube unit 86a located at the bottom of the subcooling heat exchanging unit 80, and the flat located at the top of the heat source side heat exchanging unit 40. No heat transfer fin is arranged between the tubes 45a and 45b. That is, a gap S is secured between the first heat exchange part of the refrigerant-air heat exchanger 4 and the second heat exchange part of the refrigerant-refrigerant heat exchanger 5.

(2-5) Expansion mechanisms 6a and 6b
The expansion mechanisms 6a and 6b are, for example, electric expansion valves, and before the high-pressure refrigerant cooled in the heat source side heat exchange unit 40 and the refrigerant-refrigerant heat exchanger 5 is sent to the use side heat exchangers 7a and 7b. Reduce the pressure to near low pressure in the refrigeration cycle. One ends of the expansion mechanisms 6a and 6b are connected to the supercooling heat exchange unit 80 of the refrigerant-refrigerant heat exchanger 5 through the refrigerant pipe 5a. The other ends of the expansion mechanisms 6a and 6b are connected to the use side heat exchangers 7a and 7b.

(2-6) Use side heat exchangers 7a and 7b
The use side heat exchangers 7a and 7b are heaters that heat and heat the low-pressure refrigerant decompressed by the expansion mechanisms 6a and 6b. The use side heat exchangers 7a and 7b exchange heat between the air passing outside and the refrigerant flowing in the use side heat exchangers 7a and 7b. The air flow passing through the use side heat exchangers 7a and 7b is generated by a fan (not shown). One ends of the use side heat exchangers 7a and 7b are connected to the expansion mechanisms 6a and 6b. The other ends of the use side heat exchangers 7a and 7b are connected to the suction side of the compression mechanism 2 through the refrigerant pipe 5b and the suction pipe 2a. The refrigerant pipe 5b is a refrigerant pipe that connects the use side heat exchangers 7a and 7b and the suction pipe 2a.

(2-7) Receiver 9
The receiver 9 is a container for accumulating surplus refrigerant that is generated in accordance with an operation state such as a different circulation amount of the refrigerant in the refrigerant circuit 10. The receiver 9 is a container for temporarily storing the refrigerant after passing through the first economizer refrigerant channel 71a of the economizer heat exchanging unit 70 or the first subcooling refrigerant channel 81a of the supercooling heat exchanging unit 80. is there. One end of the receiver 9 is connected to the second economizer refrigerant pipe 71 c and the other end is connected to the receiver connecting pipe 94.

(2-8) Operation The operation at the time of operation of the air conditioner 1 having the refrigerant circuit 10 as described above will be described based on the flow of the refrigerant circulating in the refrigerant circuit 10.

(2-8-1) Operation During Cooling Operation During the cooling operation, the switching mechanism 3 is controlled to the state shown by the solid line in FIG. Moreover, the opening degree of the economizer inlet expansion mechanism 79 and the suction expansion mechanism 96 is adjusted.

  First, when the compression mechanism 2 is driven, low-pressure refrigerant in the refrigeration cycle is sucked into the compression mechanism 2 from the suction pipe 2a. The low-pressure refrigerant sucked into the compression mechanism 2 is compressed to the intermediate pressure in the refrigeration cycle by the first compression element 2c and then discharged to the first intermediate refrigerant pipe 8a. The refrigerant discharged from the first compression element 2 c is sent to the intermediate heat exchange unit 60 of the refrigerant-air heat exchanger 4. The refrigerant sent to the intermediate heat exchange unit 60 is cooled by exchanging heat with the air passing outside in the intermediate heat exchange unit 60, and is sucked into the second compression element 2d through the second intermediate refrigerant pipe 8b. The Note that the refrigerant cooled by the intermediate heat exchanging unit 60 and sent to the second intermediate refrigerant pipe 8b merges with the refrigerant flowing through the economizer branch pipe 72 in the second intermediate refrigerant pipe 8b. And the refrigerant | coolant which the refrigerant | coolant cooled by the intermediate heat exchange part 60 and sent to the 2nd intermediate | middle refrigerant | coolant pipe | tube 8b and the refrigerant | coolant which flows through the economizer branch pipe 72 merged is suck | inhaled by the 2nd compression element 2d. The refrigerant sucked into the second compression element 2d is further compressed by the second compression element 2d and discharged to the discharge pipe 2b. The high-pressure refrigerant discharged from the compression mechanism 2 is sent to the heat source side heat exchange unit 40 of the refrigerant-air heat exchanger 4 through the switching mechanism 3. The high-pressure refrigerant sent to the heat source side heat exchange unit 40 is cooled by heat exchange with the air passing outside in the heat source side heat exchange unit 40. The high-pressure refrigerant cooled in the heat source side heat exchanging section 40 is sent to the economizer heat exchanging section 70 of the refrigerant-refrigerant heat exchanger 5, part of which is economizer branch pipe 72 (specifically, the first A branch is made to the economizer branch pipe 72b). The high-pressure refrigerant flowing through the first economizer branch pipe 72 b is reduced to near the intermediate pressure by the economizer inlet expansion mechanism 79 and then flows through the second economizer refrigerant flow path 72 a of the economizer heat exchanging unit 70. On the other hand, the high-pressure refrigerant flowing through the first economizer refrigerant pipe 71 b also flows through the first economizer refrigerant flow path 71 a of the economizer heat exchange unit 70. Then, in the economizer heat exchanging unit 70, heat exchange is performed between the refrigerant flowing through the first economizer refrigerant flow path 71a and the refrigerant flowing through the second economizer refrigerant flow path 72a. Specifically, the refrigerant flowing through the first economizer branch pipe 72b and flowing into the second economizer refrigerant flow path 72a of the economizer heat exchange section 70 is heated by exchanging heat with the refrigerant flowing through the first economizer refrigerant flow path 71a. Then, it flows to the second intermediate refrigerant pipe 8b through the second economizer branch pipe 72c. The refrigerant flowing through the second economizer refrigerant flow path 72a of the economizer heat exchanging section 70 and flowing into the second intermediate refrigerant pipe 8b is cooled at the intermediate heat exchanging section 60 in the second intermediate refrigerant pipe 8b. Will join. On the other hand, the refrigerant flowing through the first economizer refrigerant flow path 71a of the economizer heat exchanging section 70 is cooled by exchanging heat with the intermediate pressure refrigerant flowing through the second economizer refrigerant flow path 72a. The refrigerant cooled in the economizer heat exchange unit 70 is temporarily stored in the receiver 9. The refrigerant stored in the receiver 9 flows to the receiver connecting tube 94. Part of the refrigerant that has flowed to the receiver connection pipe 94 is branched to the suction return pipe 95. The refrigerant flowing through the suction return pipe 95 is reduced to near low pressure by the suction expansion mechanism 96 and then sent to the second subcooling refrigerant flow path 81b of the supercooling heat exchange unit 80. The refrigerant flowing through the second subcooling refrigerant channel 81b is heated by exchanging heat with the refrigerant flowing through the first subcooling refrigerant channel 81a, and flows to the suction side (suction pipe 2a) of the compression mechanism 2. On the other hand, the remaining refrigerant partially branched into the suction return pipe 95 flows into the first subcooling refrigerant channel 81a of the supercooling heat exchange unit and passes through the first subcooling refrigerant channel 81a. The refrigerant is cooled by exchanging heat with the refrigerant in the vicinity of the low pressure flowing through the second supercooled refrigerant flow path 81b and enters a supercooled state. The refrigerant cooled in the supercooling heat exchange unit 80 is sent to each of the plurality of indoor units 30a and 30b via the refrigerant pipe 5a. The refrigerant sent to the indoor units 30a and 30b is decompressed by the expansion mechanisms 6a and 6b to become a low-pressure refrigerant, and is sent to the use side heat exchangers 7a and 7b that function as a refrigerant heater. The low-pressure refrigerant sent to the use side heat exchangers 7a and 7b is heated by exchanging heat with the air passing outside. Then, the low-pressure refrigerant heated by the use side heat exchangers 7a and 7b is sucked into the first compression element 2c through the refrigerant pipe 5b and the suction pipe 2a.

(2-8-2) Operation during heating operation During the heating operation, the switching mechanism 3 is controlled to the state shown by the dotted line in FIG. Further, the economizer inlet expansion mechanism 79 and the suction expansion mechanism 96 are controlled to be closed. Therefore, the economizer heat exchanging unit 70 and the supercooling heat exchanging unit 80 are not functioning during the heating operation.

  When the compression mechanism 2 is driven in the state of the refrigerant circuit 10, the low-pressure refrigerant in the refrigeration cycle is sucked into the compression mechanism 2 from the suction pipe 2a. The low-pressure refrigerant sucked into the compression mechanism 2 is compressed to the intermediate pressure in the refrigeration cycle by the first compression element 2c and then discharged to the first intermediate refrigerant pipe 8a. The refrigerant discharged from the first compression element 2 c is sent to the intermediate heat exchange unit 60 of the refrigerant-air heat exchanger 4. The refrigerant sent to the intermediate heat exchange unit 60 is cooled by exchanging heat with the air passing outside in the intermediate heat exchange unit 60, and is sucked into the second compression element 2d through the second intermediate refrigerant pipe 8b. The The refrigerant sucked into the second compression element 2d is further compressed by the second compression element 2d and discharged to the discharge pipe 2b. The high-pressure refrigerant discharged from the compression mechanism 2 is sent to each of the plurality of indoor units 30a and 30b through the switching mechanism 3 and the refrigerant pipe 5b. The high-pressure refrigerant sent to the indoor units 30a and 30b is cooled by exchanging heat with the air passing outside in the use-side heat exchangers 7a and 7b that function as a refrigerant radiator. The high-pressure refrigerant cooled in the use-side heat exchangers 7a and 7b is decompressed by the expansion mechanisms 6a and 6b to become a low-pressure refrigerant, and after passing through the supercooling economizer heat exchange unit 70 via the refrigerant pipe 5a, It is temporarily stored in the receiver 9. The refrigerant stored in the receiver 9 passes through the economizer heat exchanging unit 70 and is then sent to the heat source side heat exchanging unit 40 of the refrigerant-air heat exchanger 4. The low-pressure refrigerant sent to the heat source side heat exchange unit 40 is heated by heat exchange with the air passing outside in the heat source side heat exchange unit 40. The high-pressure refrigerant heated in the heat source side heat exchange unit 40 is sucked into the first compression element 2c through the switching mechanism 3 and the suction pipe 2a.

(3) Detailed Configuration of Outdoor Unit 20 Hereinafter, the configuration of the outdoor unit 20 will be described with reference to FIGS. The outdoor unit 20 has a casing 20a. The casing 20a mainly includes a front plate 21 forming a front portion, a left side plate 22 forming a left portion, a back plate 23 forming a back portion, a right side plate 24 forming a right portion, and a top plate 25 forming an upper portion. The bottom plate 26 that forms the lower portion, the support columns 91 and 92 extending in the vertical direction, and the support columns 93 and 94 extending in the vertical direction are provided. The left side plate 22 and the right side plate 24 are formed integrally with the support columns 91 and 92 and the support columns 93 and 94, respectively. The side plates 22 and 24 and the back plate 23 are formed with suction ports 120a for taking air into the casing of the outdoor unit 20 (the suction ports formed in the back plate 23 are not shown). Further, the top plate 25 is formed with an outlet 120b for blowing out the conditioned air upward. The front plate 21 and the back plate 23 are attached to the outsides of the columns 91 and 94 and the columns 92 and 93, respectively. Further, the columns 91 to 94 are connected to each other by the bottom plate 26, the lateral stay 51 located at the top, and the motor support base 52 located at the top. A fan drive motor 29 a that drives the fan 29 is fixed to the motor support base 52.

  An air flow path AP is formed in the casing 20a. The air flow path AP is a flow path in which an air flow generated by the fan 29 is generated, and air that has been sucked from the suction port 120a and passed through the refrigerant-air heat exchanger 4 is formed in the upper part of the casing 20a. It is the flow path which flows toward the blower outlet 120b. Note that the air flow in the air flow path AP is indicated by arrows in FIG.

  A bell mouth 36 is disposed in the casing 20a in the vicinity of the air outlet 120b. The bell mouth 36 is formed with an opening 36a having substantially the same size as the air outlet 120b. The bell mouth 36 has a lower end fixed to the top of the lateral stay 51 and the fan motor support base 52, and is arranged so that the opening 36a is along the air outlet 120b formed in the casing 20a. Although not shown, the top plate 25 is provided with a mesh-shaped air outlet grill so as to cover the air outlet 120b.

  The bell mouth 36 mainly includes a cylindrical part 37 (corresponding to a second partition part) in which an opening 36a is formed, and a flat part 38 (first partition part) extending in the horizontal direction from the outer surface of the cylindrical part 37 to the outside. Equivalent). The tubular portion 37 extends upward (specifically, in the vertical direction) from the flat portion 38. The cylindrical portion 37 is an upper space in the casing 20a and is disposed at a substantially central portion. The bell mouth 36 is disposed such that the side surface of the cylindrical portion 37 is positioned between the refrigerant-refrigerant heat exchanger 5 and the fan 29 or fan drive motor 29a. Further, the upper surface of the cylindrical portion 37 is in contact with the top plate 25 so that the opening 36a is along the air outlet 120b.

  The flat portion 38 has one end connected to the outer surface of the cylindrical portion 37 and the other end connected to the inner surface of a plate (front plate 21, left side plate 22, back plate 23, and right side plate 24) that forms the side surface of the casing 20a. Connected to. In the present embodiment, the first header and the second header constituting the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5, respectively, are integrated. An opening (not shown) is formed at a position corresponding to the second header. The flat surface portion 38 is located below the refrigerant-refrigerant heat exchanger 5 and is located in a gap S formed between the first heat exchange portion and the second heat exchange portion. The plane portion 38 includes a front plane portion (not shown) extending from the tubular portion 37 toward the front side, a left plane portion 38b extending from the tubular portion 37 toward the left side, and a rear side from the tubular portion 37. A rear side plane portion (not shown) extending toward the right side, and a right side plane portion 38d extending toward the right side from the cylindrical portion 37. The front plane portion and the rear plane portion are in contact with the lateral stay 51 and the fan motor support base 52, and the left plane portion 38 b and the right plane portion 38 d are in contact with the lateral stay 51.

  The inner surface of the cylindrical portion 37 and the lower surface of the flat portion 38 form an air flow path AP together with the front plate 21, the left side plate 22, the back plate 23, the right side plate 24, and the bottom plate 26. That is, the bell mouth 36 guides the air after passing through the refrigerant-air heat exchanger 4 to the outlet 120b by flowing the air after passing through the refrigerant-air heat exchanger 4 through the opening 36a. Yes. The bell mouth 36 functions as a partition member that partitions the air flow path AP and the space above the refrigerant-air heat exchanger 4 by the cylindrical portion 37 and the flat portion 38. Specifically, the plane portion 38 partitions the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5 (air flow path AP) in the vertical direction. The cylindrical portion 37 partitions the side surface portion (specifically, the back side portion of the refrigerant-refrigerant heat exchanger 5) and the air flow path AP from the front of the refrigerant-refrigerant heat exchanger 5. .

  Thereby, in the casing 20a, in the space above the refrigerant-air heat exchanger 4, a partition space S1 partitioned from the air flow path AP is formed.

(4) Features FIG. 6 is a schematic diagram showing a positional relationship between a conventional refrigerant-air heat exchanger 140 and a refrigerant-refrigerant heat exchanger 150.

  Conventionally, as shown in FIG. 6, a refrigerant-refrigerant heat exchanger 150 that exchanges heat between refrigerants has an air flow that is different from that of a refrigerant-air heat exchanger 140 that exchanges heat between the refrigerant and air. It arrange | positions in the downstream of the flow direction. Therefore, during the cooling operation, the air heat-exchanged in the refrigerant-air heat exchanger 140 passes through the refrigerant-refrigerant heat exchanger 150, and the cooling efficiency in the refrigerant-refrigerant heat exchanger 150 is reduced. End up. Further, the refrigerant-refrigerant heat exchanger 150 is disposed downstream of the refrigerant-air heat exchanger 140 in the air flow direction, so that the wind speed of the air passing through the refrigerant-air heat exchanger 140 is reduced. There is a concern that the heat exchange efficiency in the refrigerant-air heat exchanger 140 also decreases. Furthermore, when the refrigerant-air heat exchanger 140 and the refrigerant-refrigerant heat exchanger 150 are arranged as described above, the occupied volume of the heat exchanger in the casing increases. In FIG. 6, 122 is a front plate, 129 is a fan, and 136 is a bell mouth.

  Therefore, in the present embodiment, first, the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5 are integrated via the first header and the second header. Thereby, the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5 can be made compact. Therefore, the occupied volume of the refrigerant-air heat exchanger 4 and the refrigerant-refrigerant heat exchanger 5 in the casing 20a can be reduced. In the present embodiment, the refrigerant-refrigerant heat exchanger 5 disposed above the refrigerant-air heat exchanger 4 is located in the partition space S1 partitioned from the air flow path AP by the bell mouth 36 as a partition member. I am doing so. Thereby, the refrigerant-refrigerant heat exchanger 5 is partitioned from the air flow path AP. Therefore, the refrigerant-refrigerant heat exchanger 5 is arranged at a position where the air after heat exchange in the refrigerant-air heat exchanger 4 hardly passes. Thereby, the fall of the cooling efficiency in the refrigerant | coolant-refrigerant heat exchanger 5 can be suppressed. Further, it is possible to suppress a decrease in the wind speed of the air after passing through the refrigerant-air heat exchanger 4, and it is possible to suppress a decrease in heat exchange efficiency in the refrigerant-air heat exchanger 4.

(5) Modifications While the embodiment of the present invention has been described with reference to the drawings, the specific configuration is not limited to the above-described embodiment, and can be changed without departing from the gist of the invention. .

(5-1) Modification A
In the above embodiment, the bell mouth 36 is described as a partition member that is partitioned from the air flow path AP, but the present invention is not limited to this.

  For example, you may comprise a partition member by the bell mouth which comprises the part corresponded to a cylindrical part, and another member which comprises the part corresponded to a plane part. Even in this case, since the partition member according to Modification A can partition the air flow path AP and the refrigerant-refrigerant heat exchanger 5, it is possible to achieve the same operational effects as in the above embodiment.

(5-2) Modification B
In addition to the configuration of the above embodiment, a heat insulating material may be arranged in the gap S2 secured between the first heat exchange unit and the second heat exchange unit. Thereby, the heat exchange between a 1st heat exchange part and a 2nd heat exchange part can be suppressed, and the heat insulation of the refrigerant | coolant-refrigerant heat exchanger 5 is ensured more. The heat insulating material may be disposed so as to cover the periphery of the refrigerant-refrigerant heat exchanger 5 in order to further secure the heat insulating property of the refrigerant-refrigerant heat exchanger 5.

(5-3) Modification C
In the said embodiment, although the air conditioning apparatus 1 which can perform air_conditionaing | cooling operation and heating operation was mentioned as an example and demonstrated as a refrigerating device, it is not restricted to this, This invention is the air which performs only air_conditionaing | cooling operation. You may apply to a harmony device and may apply to a heat pump type hot-water supply apparatus.

  The present invention can be variously applied to an outdoor unit including a refrigerant-air heat exchanger that exchanges heat between refrigerant and air, and a cold refrigerant-refrigerant heat exchanger that exchanges heat between refrigerants. is there.

4 Refrigerant-air heat exchanger 5 Refrigerant-refrigerant heat exchanger 20 Outdoor unit 20a Casing 36 Bell mouth 37 Cylindrical part (first partition part)
38 Plane part (second partition)
43a, 43b, 63a, 63b Header (first header)
44a, 44b, 64a, 64b flat tube (first flat tube)
45a, 45b, 65a, 65b Heat transfer fin (first heat transfer fin)
75a, 85a header (second header)
76aa, 76ab, 86aa, 86ab Flat tube (second flat tube)
77a, 87a Heat transfer fin (second heat transfer fin)
120b Air outlet AP Air flow path S Gap S1 Partition space

JP 2009-270748 A

Claims (4)

An outdoor unit (20) for blowing air upward,
A casing (20a) in which an air outlet (120b) for blowing out air is formed at the top;
A refrigerant-air heat exchanger (4) housed in the casing and allowing heat exchange between the refrigerant flowing in the interior and the air;
Heat exchange between refrigerants, and a refrigerant-refrigerant heat exchanger (5) housed in the casing;
With
In the casing, an air flow path (AP) that flows through the refrigerant-air heat exchanger and flows toward the outlet is formed.
A partition space (S1) that is partitioned from the air flow path by a partition member is formed in the casing and in an upper space of the refrigerant-air heat exchanger,
The refrigerant-refrigerant heat exchanger is located in the partition space;
Outdoor unit (20). A bell mouth (36) disposed in the casing in the vicinity of the outlet;
The bell mouth includes a first partition portion (37) for vertically partitioning the refrigerant-air heat exchanger and the refrigerant-refrigerant heat exchanger, and a second partition portion extending upward from the first partition portion. (38), the partition member having
The outdoor unit according to claim 1. The refrigerant-air heat exchanger is
A first header (43a, 43b, 63a, 63b) extending in the vertical direction;
Between a plurality of first flat tubes (44a, 44b, 64a, 64b) extending in a direction intersecting the first header and having an end portion connected to the first header, and each of the plurality of first flat tubes A first heat exchange section including first heat transfer fins (45a, 45b, 65a, 65b) disposed in
Have
The refrigerant-refrigerant heat exchanger is
A second header (75a, 85a) extending in the vertical direction;
Between a plurality of second flat tubes (76aa, 76ab, 86aa, 86ab) extending in a direction intersecting the second header and having an end portion connected to the second header, and each of the plurality of second flat tubes A second heat exchange portion including the second heat transfer fins (77a, 87a),
Have
The first header and the second header are integrated.
The outdoor unit according to claim 1 or 2. A gap (S) is secured between the first heat exchange part and the second heat exchange part,
In the gap, a heat insulating material is disposed,
The outdoor unit according to claim 3.

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