JP2015087038A - Heat exchanger and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger showing a high manufacturing efficiency.SOLUTION: This invention comprises a pair of header collection pipes 21 arranged to be spaced apart from each other where fluid flows; several flat pipes 23 arranged side-by-side between the pair of header collector pipes 21 where each of them is connected to the pair of header collection pipes 21 at both ends and fluid flows; partition plates 25 dividing inside the pair of header collector pipes 21 into several spaces and classifying the several flat pipes into several groups where temperatures of fluid passing through them are different to each other; flat pipes 23 of groups becoming a discharging side from a heat exchanger 20 where fluid flows; non-mounted spaces 24A formed among the flat pipes 23 and the flat pipes 23 of other groups adjacent to the flat pipes 23; and several fins 24 mounted while being connected to both flat pipes 23 between the adjoining flat pipes 23 other than the flat pipes 23 forming the non-mounted spaces 24A.

Description

  The present invention relates to a heat exchanger or the like configured by connecting a plurality of heat transfer tubes between a pair of header collecting tubes.

  Conventionally, a PFC (parallel flow type) heat exchanger having a pair of header collecting tubes, flat tubes, and fins is known. In such a heat exchanger, for example, a plurality of flat tubes each having a fluid (hereinafter referred to as refrigerant) flow path are arranged at predetermined intervals and connected to a pair of header collecting tubes. . The header collecting pipe is a pipe that distributes the refrigerant to a plurality of flat tubes and joins the refrigerant that has passed through the flat tubes. Fins for expanding the heat transfer area are installed between adjacent flat tubes and partitioned into a plurality of ventilation paths. And in a heat exchanger, the air which passes a fin and the refrigerant | coolant which flows through the inside of a flat tube heat-exchange.

  In the heat exchanger as described above, a temperature difference occurs between the refrigerant flowing on the upstream side and the refrigerant flowing on the downstream side. Also, for example, when using a heat exchanger as a condenser, the upstream side of the heat exchanger is a high-temperature and high-pressure gas refrigerant, and the downstream side is a subcooled liquid refrigerant. Phase change also occurs.

  In such a heat exchanger, for example, by dividing the inside of the header collecting pipe with a partition plate or the like, a plurality of flat tube groups with different refrigerant flow directions are formed in the heat exchanger, and a pair of headers is formed. There is one in which heat exchange is performed while flowing refrigerant between the collecting pipes. At this time, refrigerants having different temperatures flow depending on the group (area) of each flat tube. For example, if fins are installed between flat tubes adjacent to each other at the boundary (boundary) of the region, fluids having different temperatures flowing through the two flat tubes exchange heat through the fins. For example, when the heat from the refrigerant flowing in the upstream region moves to the refrigerant that has reached the supercooling region that is completely in the liquid state in the downstream region in the heat exchanger, the refrigerant in the supercooling region is again gas-liquid-refined. Loss may occur due to returning to the phase state. Thus, there was a problem that the performance of the heat exchanger was lowered.

  As a heat exchanger that avoids the problem of heat transfer in regions with different temperatures as described above, heat that prevents brazing of either one of the two flat tubes through which refrigerant of different temperatures flows and the fins An exchanger is disclosed (see, for example, Patent Document 1).

JP2012-193872A (FIG. 9)

  However, in the heat exchanger as described above, there is a possibility that a fin that has not been brazed and the flat tube come into contact with each other. For example, when trying to avoid contact between the fins that are not brazed and the flat tube during the brazing process, the gap between the flat tubes before and after the non-contact part is changed, and the fin with a changed shape is specially used. It must be prepared and the production capacity (production efficiency) is lowered.

  Then, in order to solve said problem, an object of this invention is to obtain the heat exchanger and refrigeration cycle apparatus which can avoid a heat transfer more reliably.

  A heat exchanger according to the present invention includes a pair of header collecting pipes that are arranged apart from each other and through which the fluid passes, and a pair of header collecting pipes in a heat exchanger that exchanges heat and flows out the fluid that flows in A plurality of heat transfer tubes that are arranged in parallel between each other and both ends are connected to a pair of header collecting pipes and a fluid passes through the inside, and the inside of the pair of header collecting pipes are divided into a plurality of spaces. Formed between partition plates that divide into multiple groups with different temperatures of the fluid passing through, heat transfer tubes of the group through which the fluid on the outflow side from the heat exchanger flows, and heat transfer tubes of another group adjacent to the heat transfer tubes And a plurality of fins installed to be joined to both heat transfer tubes between adjacent heat transfer tubes other than between the heat transfer tubes forming the non-installation space.

  In the present invention, a non-installation space is formed between the heat transfer tube of the group through which the fluid on the outflow side flows and the heat transfer tube of another group adjacent to the heat transfer tube. The movement can be prevented more reliably.

It is a figure which shows the structure of the refrigerating-cycle apparatus which has a heat exchanger which concerns on Embodiment 1 of this invention. It is a figure which shows the structure of the heat exchanger 20 which concerns on Embodiment 1 of this invention. It is a figure which shows the pipe internal structure of the flat tube. It is a figure which shows the flow of the refrigerant | coolant in the heat exchanger 20 which concerns on Embodiment 1 of this invention. It is a figure which shows the structure of the heat exchanger 20 which concerns on Embodiment 2 of this invention.

  Hereinafter, a heat exchanger and the like according to an embodiment of the invention will be described with reference to the drawings. In the following drawings, the same reference numerals denote the same or corresponding parts, and are common to all the embodiments described below. And the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification. In particular, the combination of the components is not limited to the combination in each embodiment, and the components described in the other embodiments can be applied to another embodiment. In addition, the upper side in the figure will be described as “upper side” and the lower side will be described as “lower side”. In the drawings, the relationship between the sizes of the constituent members may be different from the actual one.

Embodiment 1 FIG.
FIG. 1 is a diagram showing a configuration of a refrigeration cycle apparatus having a heat exchanger according to Embodiment 1 of the present invention. In FIG. 1, an air conditioner 1 will be described as a representative example of a refrigeration cycle apparatus. As shown in FIG. 1, the air conditioner 1 in the present embodiment includes an outdoor unit 2 and an indoor unit 3. And the refrigerant circuit which circulates a refrigerant | coolant and performs the air conditioning of the object space using a refrigerating cycle is comprised by connecting the outdoor unit 2 and the indoor unit 3 with piping.

  The outdoor unit 2 of the present embodiment has a compressor 10, a four-way switching valve 50, a heat exchanger 20, and an expansion valve 40. The compressor 10 sucks a low-temperature and low-pressure refrigerant, compresses the refrigerant, and discharges it in a high-temperature and high-pressure state. Although it does not specifically limit, For example, it is good to comprise the compressor 10 with the inverter compressor etc. which can control capacity | capacitance. The four-way switching valve 50 serving as a refrigerant flow switching device is a valve that switches between a refrigerant flow in the cooling operation mode and a refrigerant flow in the heating operation mode. The expansion valve 40 serving as a decompression device (a throttling device) decompresses the refrigerant to expand it.

  The heat exchanger 20 serving as an outdoor heat exchanger performs heat exchange between the refrigerant and outdoor air (outside air). For example, it functions as an evaporator during heating operation, performs heat exchange between the low-pressure refrigerant flowing from the indoor unit 3 and the outside air, and evaporates and vaporizes the refrigerant. Further, during the cooling operation, it functions as a radiator (including a condenser; the same applies hereinafter), performs heat exchange between the refrigerant compressed in the compressor 10 and the outside air, and radiates or condenses the refrigerant. Here, the heat exchanger 20 of the present embodiment is a parallel flow type (PFC) heat exchanger having a material containing aluminum such as aluminum or an aluminum alloy. The structure of the heat exchanger 20 will be described later.

  The indoor unit 3 of the present embodiment has an indoor heat exchanger 30. The indoor heat exchanger 30 performs heat exchange between the refrigerant and the air in the air-conditioning target space (room air). For example, it functions as a radiator during heating operation, and performs heat exchange between the refrigerant flowing in from the outdoor unit 2 side and room air. At this time, the indoor heat exchanger 30 dissipates or condenses the refrigerant and flows it out to the outdoor unit 2 side. On the other hand, it functions as an evaporator during cooling operation, and performs heat exchange between the refrigerant that has passed through the expansion valve 40 and room air, for example. At this time, the indoor heat exchanger 30 causes the refrigerant to take away the heat of the indoor air, evaporates it, vaporizes it, and flows it out to the outdoor unit 2 side.

  Next, operation | movement of the air conditioner 1 of this Embodiment is demonstrated based on the flow of a refrigerant | coolant. First, the cooling operation will be described. The high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 10 passes through the four-way switching valve 50 and flows into the heat exchanger 20. Then, the refrigerant (liquid refrigerant) condensed and liquefied by passing through the heat exchanger 20 and exchanging heat with outdoor air flows into the expansion valve 40. The refrigerant that has been decompressed by the expansion valve 40 and is in a gas-liquid two-phase state flows out of the outdoor unit 2.

  The gas-liquid two-phase refrigerant that has flowed out of the outdoor unit 2 passes through the piping, flows into the indoor unit 3, and passes through the indoor heat exchanger 30. For example, the refrigerant (gas refrigerant) evaporated and gasified by exchanging heat with the air in the indoor space flows out of the indoor unit 3.

  The gas refrigerant flowing out from the indoor unit 3 passes through the pipe and flows into the outdoor unit 2. Then, it passes through the four-way switching valve 50 and is sucked into the compressor 10 again. As described above, the refrigerant of the air conditioner circulates and performs air conditioning (cooling).

  Next, the heating operation will be described based on the refrigerant flow. The high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 10 passes through the four-way switching valve 50 and flows out of the outdoor unit 2. The gas refrigerant that has flowed out of the outdoor unit 2 passes through the pipe and flows into the indoor unit 3. Then, while passing through the indoor heat exchanger 30, for example, the refrigerant condensed and liquefied by exchanging heat with air in the indoor space flows out from the indoor unit 3.

  The refrigerant flowing out of the indoor unit 3 passes through the pipe and flows into the outdoor unit 2. Then, the refrigerant that has been decompressed by the expansion valve 40 and is in a gas-liquid two-phase state flows into the heat exchanger 20. Then, the refrigerant (gas refrigerant) evaporated and gasified by passing through the heat exchanger 20 and exchanging heat with outdoor air passes through the four-way switching valve 50 and is sucked into the compressor 10 again. As described above, the refrigerant of the air conditioner circulates and performs air conditioning (heating).

  FIG. 2 is a diagram showing a configuration of the heat exchanger 20 according to Embodiment 1 of the present invention. Here, in FIG. 2, the direction from the upper side to the lower side is assumed to be the direction of gravity (vertical direction). Further, the first header collecting pipe 21A and the second header collecting pipe 21B have cross sections to show the configuration inside the pipe. The heat exchanger 20 includes a first header collecting pipe 21A, a second header collecting pipe 21B, a plurality of flat tubes 23, a plurality of fins 24, a partition plate 25, and external connection pipes 26 and 27.

  In the heat exchanger 20 of the present embodiment, as described above, at least the first header collecting pipe 21A, the second header collecting pipe 21B, the flat tube 23, and the fins 24 are all members made of aluminum. The location where the first header collecting tube 21A or the second header collecting tube 21B and the flat tube 23 are in contact with each other and the location where the flat tube 23 and the fin 24 are in contact are joined together by brazing. By using the member made of the same material as the heat exchanger 20, the corrosion resistance and the like can be improved. Moreover, the lightweight heat exchanger 20 and the air conditioner 1 (outdoor unit 2) can be obtained by setting it as the material containing aluminum.

  FIG. 3 is a view showing the in-pipe structure of the flat tube 23. The flat tube 23 is a heat transfer tube whose cross-sectional outer shape is a flat shape, a wedge shape, or the like. The flat tube 23 is spaced along the direction of the flow of the air flowing into and out of the heat exchanger 20 (the direction perpendicular to the flow direction of the refrigerant flowing in the tube). Multiple columns are arranged. In the flat tube 23, as shown in FIG. 3, for example, a plurality of refrigerant channels 23A divided by partition walls are formed. Here, in this Embodiment, the heat exchanger tube is made into the flat tube 23, However, It is applicable also to the heat exchanger tube of another shape.

  A first header collecting pipe 21A and a second header collecting pipe 21B are attached to both ends of the flat tube 23. The first header collecting pipe 21A and the second header collecting pipe 21B are a pair of tubes (cylinders) having a cylindrical shape or a long cylindrical shape. In FIG. 2, the first header collecting pipe 21A is located on the right side, and the second header collecting pipe 21B is located on the left side. The first header collecting pipe 21 </ b> A and the second header collecting pipe 21 </ b> B are pipes (cylinders) that distribute the refrigerant to the flat tubes 23 that are heat transfer tubes and collect the refrigerant that has passed through the flat tubes 23. The header collecting pipes 21 and 22 have through holes (not shown) for inserting the end portions of the flat tubes 23 therein.

  In the first header collecting pipe 21 </ b> A, when the heat exchanger 20 functions as a condenser, the liquid refrigerant flows out from the external connection pipe 26 into which the gaseous refrigerant (gas refrigerant) flows from the compressor 10 and the heat exchanger 20. An external connection pipe 27 is provided. Here, considering the density difference (difference in weight) between the gas refrigerant and the liquid refrigerant, the gas refrigerant from the external connection pipe 26 located on the upper side so that the refrigerant in the heat exchanger 20 flows smoothly. So that the liquid refrigerant flows out from the external connection pipe 27 located on the lower side. However, it is not limited to this flow, and can be appropriately changed according to the arrangement state of the heat exchanger 20. In the present embodiment, the first header collecting pipe 21 </ b> A includes the external connection pipes 26 and 27, so that the pipes constituting the refrigerant circuit can generally be easily arranged in the outdoor unit 2. it can. However, the present invention is not limited to this, and the external connection pipe 26 or 27 may be provided in the second header collecting pipe 21B depending on the pipe connection situation. Here, the header collecting pipe 21 will be described below when it is not necessary to distinguish the first header collecting pipe 21A and the second header collecting pipe 21B.

  The header collecting pipe 21 has a partition plate 25 in the pipe. The partition plate 25 has a shape (for example, an oval shape) that matches the shape of the tube. The partition plate 25 partitions the inside of the pipe and divides the inside of the header collecting pipe 21 into a plurality of spaces in the vertical direction. Thus, the plurality of flat tubes 23 are divided into a plurality of groups (groups) as will be described later. In the present embodiment, the first header collecting pipe 21A has two partition plates 25 in the pipe. Then, a space for distributing the gas refrigerant flowing from the external connection pipe 26 to the plurality of flat tubes 23, a space for returning the refrigerant that has passed through the plurality of flat tubes 23 to be folded and distributed to the other plurality of flat tubes 23, and a plurality of spaces The liquid refrigerant that has passed through the flat tube 23 is merged and divided into three spaces that flow out of the external connection pipe 27. Further, the second header collecting pipe 21B has one partition plate 25 in the pipe. Then, the refrigerant that has passed through the plurality of flat tubes 23 is merged and folded, and is divided into two spaces that are distributed to the other plurality of flat tubes 23. Thus, in this embodiment, since the first header collecting pipe 21A has the external connection pipe 26 or 27, the number of partition plates 25 (the number of internal space divisions) of the first header collecting pipe 21A is One more than the number of partition plates 25 (internal space division number) of the second header collecting pipe 21B. Here, in the present embodiment, since the refrigerant is folded back also on the second header collecting pipe 21B side, the partition plate 25 is provided. However, when the folding is not required, it is not necessary to provide the partition plate 25.

  FIG. 4 is a diagram showing a refrigerant flow in the heat exchanger 20 according to Embodiment 1 of the present invention. As described above, the partition plate 25 divides the inside of the pipe into a plurality of spaces, whereby the plurality of flat tubes 23 are divided into a plurality of groups, and the temperature (state and flow direction) of the flowing refrigerant differs in each group. Thereby, the inside of the heat exchanger 20 can be divided into a plurality of regions (Sn, Sn-1, Sn-2,..., S1 from the lower stage). In this embodiment, n = 4. Therefore, it is folded three times in the heat exchanger 20 to form four refrigerant flows (four passes). The greater the number of passes, the longer the distance that the refrigerant passes through the heat exchanger 20. In order to surely flow out the subcooled refrigerant, it is preferable that the refrigerant flow has three or more passes (four or more passes when flowing in and out from the same direction).

  Here, as shown in FIG. 4, the number of the flat tubes 23 constituting each region may not be the same. Here, in order to increase the flow rate of the refrigerant flowing out from the heat exchanger 20, the number of flat tubes 23 constituting the region S4 is the smallest, and the region S3, the region S2, and the region S1 increase in this order. It can be arbitrarily set depending on the position of the partition plate 25.

  Moreover, the heat exchanger 20 has fins 24 having a shape such as an uneven shape (corrugated) or a wave shape (wave) between the flat tube 23 and the flat tube 23. By providing the fins 24 between the flat tubes 23 and expanding the heat transfer area, the efficiency of heat exchange between the refrigerant and the air can be increased.

  In the present embodiment, as shown in FIG. 2, the boundary between the region S4 where the refrigerant (the refrigerant flowing in the most downstream path) that flows out from the external connection pipe 27 flows and the region S3 adjacent to the region S4 ( Between the two flat tubes 23 at the boundary), a space in which an object that thermally connects the two flat tubes 23 such as the fins 24 is not installed is formed. This space is defined as a non-installation space 24A. The non-installation space 24 </ b> A is formed by the heat of the refrigerant in the region S <b> 3 passing through the fins 24 to the refrigerant in the region S <b> 4 that is supercooled and about to flow out of the external connection pipe 27 due to heat exchange with air. In this way, the heat exchanger 20 as a whole forms a space where the heat exchange efficiency deteriorates, such as a refrigerant with insufficient supercooling flowing out, a phase change occurs, and a gas refrigerant is generated. This is to force it down. This configuration is easily realized by providing the non-installation space 24A without installing the fins 24 or the like between the two flat tubes 23 serving as the boundary between the region S3 and the region S4 when the heat exchanger 20 is manufactured. can do. Here, the size of the non-installation space 24 </ b> A (interval between the flat tubes 23) can be arbitrarily set as long as heat transfer between the two flat tubes 23 does not occur. However, when the heat exchanger 20 is produced, a special setting or the like may be required if the interval is changed. In consideration of production efficiency and the like, it is preferable that the interval be the same as the interval between the other flat tubes 23 to which the fins 24 are attached.

  For example, heat transfer between the regions via the fins 24 also occurs at the fins 24 at the boundary between the region S1 and the region S2 and at the boundary between the region S2 and the region S3. However, in these regions, the refrigerant is in a gas-liquid two-phase state, and the temperature difference of the refrigerant between the regions is small. In the next pass, it is possible to perform condensation or the like by heat exchange with air. For this reason, the effect of heat dissipation by providing the fins 24 and expanding the heat transfer area is greater than the loss due to heat transfer through the fins 24. Therefore, in the heat exchanger 20 of the present embodiment, at least the fins 24 and the like are not attached between the flat tubes 23 that are the boundary between the region S3 and the region S4, and a non-installation space 24A is provided. However, it is not limited to this. For example, as described above, when the loss due to the heat transfer through the fin 24 is smaller than the effect of heat dissipation due to the expansion of the heat transfer area of the fin 24, the fin 24 and the like are attached at the boundary of other regions. It may not be possible.

  As described above, according to the first embodiment, in the plurality of flat tubes 23, in the heat exchanger 20 through which refrigerants having different temperatures pass, the fins 24 are provided between the flat tubes 23 through which the refrigerants having different temperatures flow. By setting the non-installation space 24 </ b> A in which no etc. are installed, the space between the two flat tubes 23 can be more reliably thermally separated and the heat transfer via the fins 24 and the like can be suppressed. In particular, the non-installation space 24A is formed between the flat tube 23 serving as a boundary between the region in the heat exchanger 20 where the most downstream refrigerant flows and the region where the upstream refrigerant flows. The heat exchanger 20 can be allowed to flow out without being heated, and the heat exchange performance can be enhanced. For this reason, when using the heat exchanger 20 as a condenser, the sufficiently subcooled refrigerant can be allowed to flow out without the supercooled refrigerant being heated again. And in production of such a heat exchanger 20, since it can implement | achieve only by not attaching the fin 24 between the flat tubes 23 which are going to form the non-installation space 24A, production efficiency can be made high. .

Embodiment 2. FIG.
FIG. 5 is a diagram showing a configuration of the heat exchanger 20 according to Embodiment 2 of the present invention. In Embodiment 1 described above, the heat exchanger 20 is configured only by the PFC heat exchanger. The heat exchanger 20 according to the present embodiment is configured such that, in the heat exchanger 20, the most downstream flow path close to the refrigerant outflow side is configured by a cross fin and tube heat exchanger 28. . When the heat exchanger 20 is used as a condenser, liquid refrigerant flows through the cross fin and tube heat exchanger 28.

  In FIG. 5, the same reference numerals as those in FIG. 2 perform the same operations and functions as those described in the first embodiment. In FIG. 5, a cross fin and tube heat exchanger 28 has, for example, a copper heat transfer tube 28A and a fin 28B made of a material containing aluminum. Heat transfer tubes 28A are provided so as to penetrate through holes (not shown) provided in the fins 28B with respect to the plurality of fins 28B arranged at predetermined intervals. For example, the heat transfer tube 28 </ b> A is bent into a hairpin shape, a plurality of heat transfer tubes 28 </ b> A are connected by a U-bend or the like to form one flow path, and are connected to the external connection pipe 27. Since there is one flow path, no distribution loss occurs. Here, in FIG. 5, the PFC heat exchanger has the partition plate 25 and is divided into a plurality of regions as in the first embodiment, but the partition plate 25 may not be provided in some cases. .

  Moreover, in the heat exchanger 20, since the PFC heat exchanger part and the cross fin and tube heat exchanger 28 are thermally separated, heat transfer between refrigerants having different temperatures in the heat exchanger 20 is achieved. Does not occur. Here, in FIG. 5, in the heat exchanger 20, the cross fin and tube type heat exchanger 28 is installed at a position below the PFC heat exchanger, but is not limited to the installation position. If it is downstream in the flow of the refrigerant, for example, it may be installed at a position above the PFC heat exchanger.

Embodiment 3 FIG.
In the first and second embodiments, the use of the heat exchanger 20 as a condenser has been basically described. The heat exchanger 20 is particularly effective when used as a condenser, but the use is not particularly limited. For example, in the case of the air conditioner 1 described in the first embodiment, the flow direction of the refrigerant is changed. By switching, the heat exchanger 20 can be used as an evaporator.

  Moreover, in said Embodiment 1 and 2, although the fluid which passes the inside of the heat exchanger 20 was used as the refrigerant | coolant, it is applicable also to another fluid.

  The above-described refrigeration cycle apparatus according to Embodiment 1 can be applied to apparatuses that use a refrigeration cycle (heat pump cycle), such as a refrigeration apparatus, an air conditioner, and a hot water supply apparatus.

  1 air conditioner, 2 outdoor unit, 3 indoor unit, 10 compressor, 20 heat exchanger, 21 header collecting pipe, 21A first header collecting pipe, 21B second header collecting pipe, 23 flat tube, 23A refrigerant flow path, 24 fin, 24A non-installation space, 25 partition plate, 26, 27 external connection piping, 28 cross fin and tube type heat exchanger, 28A heat transfer tube, 28B fin, 30 indoor heat exchanger, 40 expansion valve, 50 four-way switching valve .

Claims (5)

In the heat exchanger that exchanges heat and flows out the fluid that flows in,
A pair of header collecting tubes that are spaced apart from each other and through which fluid passes;
A plurality of heat transfer tubes that are arranged in parallel between the pair of header collecting pipes, both ends of which are connected to the pair of header collecting pipes, and a fluid passes through the inside;
A partition plate that divides the inside of the pair of header collecting pipes into a plurality of spaces, and divides the plurality of heat transfer tubes into a plurality of groups having different temperatures of fluids passing therethrough,
A non-installation space formed between the heat transfer tube of the group through which the fluid on the outflow side from the heat exchanger flows and the heat transfer tube of another group adjacent to the heat transfer tube;
A heat exchanger comprising: a plurality of fins that are installed to be joined to both heat transfer tubes between adjacent heat transfer tubes other than between the heat transfer tubes forming the non-installation space.   The heat exchanger according to claim 1, wherein the heat transfer tube is a flat tube.   The heat exchanger according to claim 1 or 2, wherein the plurality of heat transfer tubes are divided into three or more groups. In the heat exchanger that exchanges heat and flows out the fluid that flows in,
A pair of header collecting pipes that are spaced apart from each other and through which the fluid passes, and are arranged in parallel between the pair of header collecting pipes, both ends of which are connected to the pair of header collecting pipes so that fluid flows inside. A parallel flow heat exchanger having a plurality of flat tubes passing therethrough;
A pipe is connected on the downstream side of the parallel flow heat exchanger, and fins are inserted and fixed to the heat transfer tubes at arbitrary intervals, and the refrigerant passing through the heat transfer tubes and the air passing between the fins A heat exchanger comprising a fin-and-tube heat exchanger for performing heat exchange. A compressor for compressing the refrigerant;
A condenser having the heat exchanger according to any one of claims 1 to 4, and condensing the refrigerant compressed by the compressor;
Throttle means for depressurizing the refrigerant condensed by the condenser;
A refrigeration cycle apparatus that constitutes a refrigerant circuit that circulates the refrigerant by connecting a pipe to an evaporator that evaporates the refrigerant decompressed by the throttling means by heat exchange and cools a fluid to be cooled.

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