JP2012093091A - Heat exchanger and refrigeration air conditioning device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high-performance heat exchanger that is compact and reduced in pressure loss of fluid, along with a refrigeration air conditioning device.SOLUTION: A first flat tube and a second flat tube are laminated and arranged to contact with each other on a flat surface and so that a flow direction of low-temperature fluid and a flow direction of high temperature fluid are parallel to each other. In addition, at least one of the flat tubes between the first flat tube and the second flat tube is constituted of a plurality of flat tubes aligning in a laminating direction, and both ends of the plurality of flat tubes are bent in a direction perpendicular to both respective flow directions and the laminating direction and along the flat surface so that both ends of the first flat tube and both ends of the second flat tube do not cross with each other.

Description

The present invention relates to a heat exchanger for transferring heat from a high temperature fluid to a low temperature fluid by exchanging heat between the low temperature fluid and the high temperature fluid. The present invention also relates to a refrigeration air conditioner using this heat exchanger.

A conventional heat exchanger includes a flat first flat tube having a plurality of through holes through which a low temperature fluid flows, a flat second flat tube having a plurality of through holes through which a high temperature fluid flows, and a first flat tube. A first header connected to both ends and a second header connected to both ends of the second flat tube are provided, and the first flat tube and the second flat tube are parallel in the longitudinal direction (fluid flow direction). Thus, high heat exchange performance is obtained by making the flat surfaces contact and laminate each other (see, for example, Patent Document 1).

JP 2002-340485 (pages 4-5, FIG. 1)

A conventional refrigeration air conditioner using a conventional heat exchanger as described above is configured such that an HFC (hydrofluorocarbon) refrigerant circulates by connecting a compressor, a radiator, a flow rate control means, and an evaporator with refrigerant piping. However, recently, since HFC refrigerants cause global warming, refrigerants such as carbon dioxide having a low global warming potential have been used instead. However, when carbon dioxide is used as a refrigerant, there is a problem that heat exchange performance is extremely small as compared with the conventional case.

In such a heat exchanger, in order to obtain high heat exchange performance, the contact area is increased by increasing the length (length in the fluid flow direction) or width of the first flat tube and the second flat tube. Therefore, the heat exchanger is two-dimensionally enlarged. Further, when the heat exchange performance is improved by increasing the flow rates of the low-temperature fluid and the high-temperature fluid, it is necessary to suppress an increase in pressure loss due to an increase in the flow velocity in the pipe, which includes the width of the first flat tube and the second flat tube. Since it can only be adjusted in the width direction, such as by increasing the pressure, the pressure loss cannot be sufficiently suppressed if the adjustment in the length direction is also performed, and this causes an increase in the power of the drive device for sending and circulating the fluid to the heat exchanger. was there.

Further, when the number of parallel flow paths increases as in the case of increasing in the width direction, the first header and the second header
When fluid is distributed to each flow path with the header, flow rate deviation due to flow resistance difference is likely to occur, especially when the fluid is a gas-liquid two-phase flow state where the gas phase and liquid phase are mixed. Also, there arises a problem that bias occurs. As a result, there has been a problem that the flow rate of the fluid that can effectively exchange heat is excessive and insufficient, the temperature efficiency is remarkably lowered, the pressure loss is increased, and the heat exchange performance is lowered.

Furthermore, in the conventional heat exchanger described in the above-mentioned patent document, increasing the contact area by stacking the first flat tube and the second flat tube in the stacking direction is the difference between the first header and the second header. There was a problem that it was difficult because of interference.

The present invention has been made to solve the above-described problems, and an object of the present invention is to obtain a high-performance heat exchanger that is compact and has a small fluid pressure loss.
Moreover, it aims at obtaining a high-performance and compact refrigeration air conditioner.

The heat exchanger according to the present invention includes a flat first flat tube having a through hole through which a low-temperature fluid flows;
A flat second flat tube having a through-hole through which a high-temperature fluid flows, a first inlet header and a first outlet header connected to both ends of the first flat tube, and both ends of the second flat tube, respectively. A heat exchanger having a second inlet header and a second outlet header, wherein the first flat tube and the second flat tube are in contact with each other on a flat surface, and the low fluid The flow direction of the high-temperature fluid and the flow direction of the high-temperature fluid are stacked so as to be parallel to each other, and at least one flat tube of the first flat tube and the second flat tube is a plurality arranged in the stacking direction. The both ends of the plurality of flat tubes are connected to the fluid flow direction and the stacking direction so that the both ends of the first flat tube and the both ends of the second flat tube do not intersect each other. Bending in a direction perpendicular to any of Is obtained by a parallel flow path above a plurality of flat tubes, the inlet header and outlet header respectively provided at both ends of the plurality of flat tubes.

In the heat exchanger according to the present invention, both ends of the plurality of flat tubes are arranged in either the flow direction or the stacking direction of each fluid so that the both ends of the first flat tube and the both ends of the second flat tube do not intersect each other. Since the first flat tube and the second flat tube are alternately laminated so that the flow directions are parallel to each other, headers connected to both ends of each flat tube are provided. There is no interference.

It is a figure which shows the heat exchanger by Embodiment 1 of this invention. It is a systematic diagram which shows the refrigerating air conditioner using the heat exchanger by Embodiment 1 of this invention. It is a pressure-enthalpy diagram of carbon dioxide for explaining operation of the heat exchanger of Embodiment 1 of the present invention. It is a systematic diagram which shows another refrigeration air conditioning apparatus using the heat exchanger by Embodiment 1 of this invention. It is a systematic diagram which shows another refrigeration air conditioning apparatus using the heat exchanger by Embodiment 1 of this invention. It is a figure which shows the heat exchanger by Embodiment 2 of this invention. It is sectional drawing which shows another tubular header concerning Embodiment 2 of this invention. It is a figure which shows another tubular header concerning Embodiment 2 of this invention. It is sectional drawing which shows another tubular header concerning Embodiment 2 of this invention. It is a figure which shows the heat exchanger by Embodiment 3 of this invention. It is a figure which shows the heat exchanger by Embodiment 4 of this invention. It is a figure which shows the heat exchanger by Embodiment 5 of this invention. It is a figure which shows the heat exchanger by Embodiment 6 of this invention. It is a figure which shows the heat exchanger by Embodiment 7 of this invention. It is a figure which shows the heat exchanger by Embodiment 8 of this invention. It is a figure which shows the heat exchanger by Embodiment 9 of this invention. It is a figure which shows the heat exchanger by Embodiment 10 of this invention.

Embodiment 1 FIG.
1 is a view showing a heat exchanger 10 according to Embodiment 1 of the present invention, in which FIG. 1 (a) is a front view, FIG. 1 (b) is a side view in the direction of arrow b in FIG. 1 (c) is a cross-sectional view taken along line cc in FIG. 1 (a), and FIG. 1 (d) is a cross-sectional view taken along line dd in FIG. 1 (b).
In the figure, each of the first flat tube 1 and the second flat tube 2 has a plurality of through-holes through which a low-temperature fluid and a high-temperature fluid flow. The fluid flows in the plane where the first flat tube and the second flat tube are in contact with each other in the direction of flow (L direction).
The first flat tube 1 includes three first flat tubes 1a, 1b, 1c, and second arranged in the stacking direction (S direction).
The flat tube 2 is composed of two second flat tubes 2a and 2b arranged in the stacking direction (S direction), and both ends of the first flat tubes 1a, 1b and 1c and both ends of the second flat tubes 2a and 2b are stacked. The first flat tubes 1a, 1b, 1c and the second flat tubes 2a, 2b are bent at predetermined angles along the flat surfaces so that they do not overlap when viewed from the direction. That is, both the end portions of the first flat tubes 1a, 1b, 1c and the both end portions of the second flat tubes 2a, 2b are respectively in the longitudinal direction (L direction) and the stacking direction (S direction).
And both ends of the first flat tube 1 and the both ends of the second flat tube 2 are bent so as not to cross each other.
The first flat tubes 1a, 1b, and 1c are connected to the first inlet header 3 and the first outlet header 4 at both ends, respectively, and constitute a parallel flow path.
Further, the two second flat tubes 2a and 2b are connected to the second inlet header 5 and the second outlet header 6 at both ends, respectively, to constitute a parallel flow path.
Furthermore, the flow passage cross-sectional area (cross-sectional area perpendicular to the fluid flow direction) or number of the through hole of the first flat tube 1 is configured to be larger than that of the second flat tube 2, and the total flow area of the first flat tube 1 is It is larger than the second flat tube.

Further, at least one of the first inlet header 3, the first outlet header 4, the second inlet header 5, and the second outlet header 6 is a tube-shaped tubular header that is open at both ends (in FIG. The header is a tubular header), as shown in FIG. 1 (c) and FIG. 1 (d),
A plurality of flat tubes 1a, 1b, 1c (or 2a, 2b) constituting a parallel flow path are bundled, and a plurality of flat tubes constituting a parallel flow path with the tube axis direction A of the tubular header are formed at the opening end of the tubular header. The flow direction of the fluid is connected so as to be the same direction.
Moreover, in this Embodiment, as shown in FIG.1 (d), the edge part of several flat tube 1a, 1b, 1c is bent in the lamination direction, and it piles up in the thickness direction of a flat tube, and opens the tubular header. Connected to the end.
Moreover, in this Embodiment, the 1st inlet header 3 is installed so that the pipe-axis direction A may become a perpendicular direction.

The material of the first flat tube 1 and the second flat tube 2 is 1000 such as A1050 and A1070.
The material of the base, aluminum alloys such as 3000 series such as A3003, and 6000 series, and steels such as stainless steel and carbon steel are joined by brazing or the like.

In FIG. 1C, the tube ends of the flat tubes 1a, 1b, and 1c are connected flush with the inner wall when viewed from the inside of the tubular header, but may be connected by protruding or retracting.

In addition, according to the configuration of the present embodiment, both ends of the first flat tube and both ends of the second flat tube are bent along a flat surface. You may bend along a flat surface so that the both ends of a 1st flat tube and the both ends of a 2nd flat tube may not overlap seeing from a lamination direction.

Moreover, in this Embodiment, although the 1st flat tube 1 and the 2nd flat tube 2 showed in the example of three and two, if one side is plurality, it will not restrict to this number, 1st The flat tube 1 and the second flat tube 2 may be laminated and arranged in a number of three or more.
Moreover, although the case where the through-holes of the first flat tube 1 and the second flat tube 2 are arranged in a row is shown here, the through-holes need not be in a row, and may be in a plurality of rows.
Moreover, although the shape of the through hole is rectangular, it may be circular, and the heat transfer area can be increased by forming protrusions on the inner surface to further improve the heat exchange characteristics.

Needless to say, a heat exchanger similar to that of the present embodiment can be configured even if thin tubes having through holes are used side by side instead of a flat tube.

In FIG. 1, FC indicates a low-temperature fluid flow, and FH indicates a high-temperature fluid flow. Cryogenic fluid is first
In the order of the inlet header 3, the first flat tube 1, and the first outlet header 4, the high-temperature fluid flows in the order of the second inlet header 5, the second flat tube 2, and the second outlet header 6. Both fluids exchange heat through the contact surface with the flat tube 2.

According to the configuration of the present embodiment, both ends of the first flat tube or both ends of the second flat tube are arranged so that both ends of the first flat tube and both ends of the second flat tube do not overlap when viewed from the stacking direction. Since the first flat tube and the second flat tube are alternately laminated so that the flow directions thereof are parallel, the first flat tube connected to the first flat tube is configured by bending along a flat surface. Since the first header and the second header connected to the second flat tube do not interfere with each other, a plurality of flat tubes can be stacked in the stacking direction to increase the contact area. As a result, the heat exchange performance can be improved, and the heat exchanger becomes compact without being two-dimensionally enlarged.

In addition, since the first header and the second header do not interfere with each other, the plurality of first flat tubes and the plurality of second flat tubes arranged in the stacking direction can be configured to be parallel flow paths, respectively. The heat exchange characteristics can be increased by increasing the fluid flow rate without increasing the pressure loss. Further, there is no increase in power of the driving device for sending and circulating the fluid to the heat exchanger.

Furthermore, the header connected to the flat tubes constituting the parallel flow path is a tubular header, and the through hole of each flat tube at the open end of the tubular header (the connection portion between the flat tube and the tubular header) is the other side of the tubular header. Therefore, the flow resistance difference with respect to each through hole is small, and the fluid is evenly distributed or mixed. For this reason, the temperature efficiency of the fluid can be maximized, the pressure loss can be minimized, and the heat exchange performance can be increased.

Also, so that both ends of the first flat tube and both ends of the second flat tube do not overlap when viewed from the stacking direction,
Both ends of the first flat tube or the second flat tube are bent along a flat surface, and both ends of the plurality of first flat tubes and the both ends of the plurality of second flat tubes are compared with each other. When connecting to a tubular header, the ends of each flat tube are bent in the stacking direction, making it easy to route the pipes for bundling the ends of the flat tubes in one place. The whole can be configured compactly.
In addition, since an increase in the amount of refrigerant used can be suppressed, a compact and highly environmental heat exchanger can be provided.

Moreover, according to the structure of this Embodiment, since the direction of the flow of a low temperature fluid and a high temperature fluid can be made to oppose, temperature efficiency can increase and heat exchange performance can be increased.

Further, in the present embodiment shown in FIG. 1, the direction of bending both ends of the first flat tube and the second flat tube is opposite to the W direction between the first flat tube and the second flat tube, Since the first flat tube and the second flat tube can be configured by using the same flat tube whose both ends have the same bending angle and being vertically inverted, the manufacturing process and management can be simplified.

Furthermore, to increase the heat exchange performance by increasing the flow rate, in order to suppress the pressure loss,
It is necessary to enlarge the inner diameter of the header so as to achieve an appropriate flow rate, and in order to maintain pressure resistance, the wall thickness increases and the outer diameter increases remarkably, but the header is made of high-strength steel, so the outer The increase in diameter can be suppressed, and it is effective for downsizing the entire heat exchanger

In addition, steel such as stainless steel and carbon steel that make up the header can be brazed and joined to aluminum alloys, copper, and copper alloys without generating weakly fragile compound layers. 10 can be attached to copper pipes generally used in home air conditioners and commercial air conditioners by brazing or the like.

Furthermore, since the flat tube is made of an aluminum alloy, it can be attached to the header relatively easily by brazing or the like, and the aluminum alloy can be manufactured by extrusion molding at a relatively low cost. Can be suppressed.
In addition, the relatively high-strength aluminum alloys in the 3000s and 6000s can be made thinner, so that the size and cost can be reduced.

FIG. 2 is a diagram showing a refrigeration air conditioner using the heat exchanger of the first embodiment, and FIG.
Is a system diagram, and FIGS. 2B and 2C are a perspective view and a top view of the internal structure, respectively.
In FIG. 2 (a), the refrigerant circuit of the present refrigeration air conditioner is a refrigerant circuit in which carbon dioxide is used as a refrigerant, and a compressor 20, a radiator 21, a decompressor 22, and a cooler 23 are connected in order.
The first inlet header 3 and the cooler 23 of the heat exchanger 10, the first outlet header 4 and the compressor 20, the second inlet header 5 and the radiator 21, and the second outlet header 6 and the decompressor 22 are connected to each other. ing. Further, the first inlet header 3 is constituted by a tubular header, and the first outlet header 4
Each of the second inlet header 5 and the second outlet header 6 is a tubular header, or
A pipe axis is comprised by the branch branch header orthogonal to the flat surface of the some flat tube which comprises a parallel flow path. In the case of a branch and branch header, the plurality of flat tubes are connected to the side of the header.

The low-temperature and low-pressure vapor refrigerant in the refrigerant piping of the compressor 20 is compressed by the compressor 20 and discharged as a high-temperature and high-pressure supercritical fluid. This refrigerant is sent to the radiator 21 where heat is exchanged with air or the like to lower the temperature and become a high-pressure supercritical fluid. This refrigerant is cooled by the heat exchanger 10 to lower its temperature, flows into the decompression device 22, is decompressed, changes to a low-temperature low-pressure gas-liquid two-phase flow state, and is sent to the cooler 23. The cooler 23 evaporates by exchanging heat with air or the like, becomes low-temperature and low-pressure refrigerant vapor, is further heated by the heat exchanger 10, and returns to the compressor 20.

2 (b) and 2 (c), the refrigeration air conditioner is installed outside the compressor 20, the radiator 2 and the like.
1 and the outdoor unit in which the heat exchanger 10 is housed, the decompression device 22 installed in the room, and the cooler 23 are connected by a pipe. Heat is radiated from the radiator 21 by the ventilation of the fan 24 of the outdoor unit.
Here, the heat exchanger 10 uses the heat exchanger of the first embodiment, and each flat tube is made of a material having a relatively large ductility such as an aluminum alloy, copper and a copper alloy, or a thin flexible tube. The first flat tube 1 and the second flat tube 2 are both joined with a flat surface in parallel with the longitudinal direction (L direction) aligned, and the header is connected to both ends. Since the longitudinal direction can be freely bent in the laminating direction with relatively low rigidity, when mounted in an outdoor unit, as shown in the figure, it is placed around the shell of containers such as the compressor 20. It can be arranged, or the space between the container and the pipe can be used effectively, so that the mounting efficiency to the apparatus is improved and the entire apparatus is reduced in size.

FIG. 3 is a pressure-enthalpy diagram of carbon dioxide. In the figure, point A represents the state of the refrigerant at the radiator inlet, point B represents the state of the refrigerant at the radiator outlet, and point C represents the state of the refrigerant at the inlet of the decompression device. In order to dissipate heat above the critical point using carbon dioxide as a refrigerant in a refrigeration air conditioner, the efficiency is greatly improved by heat exchange in a region where the specific heat near the critical point is extremely large (the region surrounded by the thick line D in the figure). Although the temperature can be improved, when the outside air temperature is high, the outlet temperature of the radiator 21 cannot be lowered sufficiently. However, in the heat exchanger 10, the low-temperature refrigerant including the refrigerant liquid at the cooler outlet 23 efficiently cools the refrigerant flowing from the radiator 21 outlet to the decompressor 22 inlet. It can be lowered sufficiently.

In the heat exchanger 10, the pressure loss when the low-temperature gas-liquid two-phase refrigerant containing the refrigerant liquid flows through the first flat tube 1 is that the high-temperature and high-pressure supercritical refrigerant flows through the second flat tube 2. However, since the flow passage cross-sectional area or number of the through hole of the first flat tube 1 is larger than that of the second flat tube 2, the flow rate in the first flat tube can be suppressed, so that the flow rate is appropriate. Pressure loss can be maintained. Moreover, since it is not the structure which enlarges in a length direction and increases a contact area, a pressure loss can be kept appropriate.

In addition, since the first inlet header 3 is constituted by a tubular header and the gas-liquid two-phase refrigerant flows into the first inlet header 3, the refrigerant has a small flow path resistance difference to each through hole. In addition to being easily distributed appropriately, the gas-liquid ratio of the fluid flowing into each through hole can be made uniform by mixing the gas-liquid inside the header.
Furthermore, since the first inlet header 3 constituted by the tubular header is arranged so that the tube axis direction is the vertical direction, there is no difference in the gravity acting on the fluid flowing to each through hole, so the gas-liquid ratio The influence which it has on can be suppressed. For this reason, the temperature efficiency of the fluid can be maximized, the pressure loss can be minimized, and the heat exchange performance can be increased.
In addition, when the 2nd inlet header 5 is comprised with a tubular header and a gas-liquid two-phase refrigerant | coolant flows in into this 2nd inlet header 5, there exists the same effect in the 2nd inlet header 5. FIG.

FIG. 4 is a system diagram of another refrigerating and air-conditioning apparatus using the heat exchanger according to the first embodiment. A refrigerant circuit in which the compressor 20, the radiator 21, the decompressor 22, and the cooler 23 are connected in order, one end is connected between the radiator 21 and the decompressor 22, and the other end is a refrigerant compression process in the compressor 20. A bypass pipe 32 connected to an injection port 33 provided in the middle of the heat exchanger 10, and a second pressure reducing device 31 provided in the middle of the bypass pipe 32, and a first inlet header 3 (tubular header) of the heat exchanger 10. And the second decompressor 31, the first outlet header 4 and the injection port 33, the second inlet header 5 and the radiator 21, and the second outlet header 6 and the decompressor 22 are respectively connected.

The refrigerant decompressed by the second decompression device 31 changes to a low-temperature gas-liquid two-phase flow state, passes through the heat exchanger 10, and is sent to the injection port 33 of the compressor 20. In the heat exchanger 10, the low-temperature refrigerant containing the refrigerant liquid from the outlet of the second pressure reducing device 31 is supplied from the outlet of the radiator 21 to the pressure reducing device 2.
In order to efficiently cool the refrigerant flowing to the inlet 2, the refrigerant temperature at the inlet of the decompression device 22 can be sufficiently lowered as in the refrigeration air conditioner shown in FIG. 2.

FIG. 5 is a diagram showing still another refrigerating and air-conditioning apparatus using the heat exchanger according to the first embodiment.
5A is a system diagram, and FIGS. 5B and 5C are a perspective view and a top view of the internal structure, respectively.
In FIG. 5A, the refrigerant circuit of the refrigeration air-conditioning apparatus is a refrigerant circuit in which a compressor 20, a radiator 21, a decompressor 22, and a cooler 23 are connected in order, and the second inlet of the heat exchanger 10. The header 5 (tubular header), the radiator 21, the second outlet header 6, and the pressure reducing device 22 are connected. The first outlet header 4, the auxiliary compressor 40, the auxiliary condenser 41, and the auxiliary pressure reducing device 42
The first inlet header 3 has a second refrigerant circuit connected in order. The second refrigerant circuit is H
It is configured to operate in a vapor compression refrigeration cycle using FC refrigerant, HC refrigerant or ammonia.

The refrigerant decompressed by the auxiliary decompression device 42 changes to a low-temperature gas-liquid two-phase flow state, passes through the heat exchanger 10, and returns to the auxiliary compressor 40. In the heat exchanger 10, the low-temperature refrigerant containing the refrigerant liquid from the outlet of the auxiliary decompression device 42 efficiently cools the refrigerant flowing from the outlet of the radiator 21 to the inlet of the decompression device 22. Similarly to the refrigeration air conditioner shown in FIG.

5 (b) and 5 (c), the refrigeration air conditioner is installed outside the compressor 20, the radiator 2 and the like.
1, an outdoor unit in which an auxiliary compressor 40, an auxiliary condenser 41, an auxiliary pressure reducing device 42, and a heat exchanger 10 are housed, a pressure reducing device 22 installed in a room, and a cooler 23 are connected by piping. Yes. Heat is radiated from the radiator 21 by the ventilation of the fan 24 of the outdoor unit.
Here, the heat exchanger 10 uses the heat exchanger of the first embodiment, and each flat tube is made of a material having a relatively large ductility such as an aluminum alloy, copper and a copper alloy, or a thin flexible tube. The first flat tube 1 and the second flat tube 2 are both joined with a flat surface in parallel with the longitudinal direction (L direction) aligned, and the header is connected to both ends. Since the longitudinal direction can be freely bent in the laminating direction with relatively low rigidity, when mounted in a unit, as in FIGS. 2 (b) and 2 (c), around the shell of containers such as a compressor It is possible to arrange them in line with each other, or to effectively use the space between the container and the piping, which increases the mounting efficiency of the apparatus and contributes to the downsizing of the entire apparatus.
5B and 5C, in addition to the compressor 20 and the auxiliary compressor 40, in the case of a unit in which a liquid reservoir container 43 that adjusts the amount of refrigerant in the refrigerant circuit to an appropriate amount is added. This is an example in which the heat exchanger 10 is installed around the liquid reservoir container 43. As the number of containers increases, the degree of freedom of installation space increases, which contributes to improved mounting efficiency.

Further, in FIG. 5, the radiator 21 can be omitted, and it can be applied to a so-called secondary loop refrigeration air conditioner that cools all the high-temperature and high-pressure gas discharged from the compressor 20 with the heat exchanger 10. In the heat exchanger 10, the required heat exchange amount is increased, and the volume ratio of the entire refrigeration air conditioner is relatively increased. Therefore, the effect of making the heat exchanger 10 compact is further enhanced.
Note that the refrigeration air conditioners shown in FIGS. 2, 4 and 5 can be applied to stationary refrigeration air conditioners such as room air conditioners, packaged air conditioners, water heaters, and refrigerators.

As described above, in the refrigerating and air-conditioning apparatus using the heat exchanger according to the present embodiment, at least one of the low-temperature fluid and the high-temperature fluid flowing through the first flat tube and the second flat tube of the heat exchanger is gas-liquid. The first inlet header or the second inlet header through which the fluid in the gas-liquid two-phase state flows is configured by a tubular header, and the laminated flat tubes are bundled at one place at the outlet end of the tubular header. Since they are connected, the difference in flow path resistance to each through hole is small, so that proper distribution is easy. Moreover, the gas-liquid ratio of the fluid flowing into each through hole can be made uniform by the gas-liquid mixing inside the tubular header.
In addition, since this tubular header is arranged so that the tube axis direction is the vertical direction, there is no difference in the gravity acting on the fluid flowing through each through hole, so that the fluid flows properly to each through hole of the flat tube. It is possible to maximize the temperature efficiency of the fluid, to minimize the pressure loss, and to increase the performance of the heat exchanger.

In addition, for a refrigeration air conditioner using carbon dioxide as a refrigerant, the high-temperature fluid flowing through the second flat tube of the heat exchanger is a high-temperature and high-pressure supercritical fluid, and the low-temperature fluid flowing through the first flat tube is a gas-liquid two-phase fluid. So that the heat exchanger can be optimally configured according to the heat exchanger conditions such as temperature and flow rate conditions,
It is possible to maximize the performance of the heat exchanger and thus improve the performance of the equipment.
In addition, since the heat exchanger can be configured in a compact manner and an increase in the amount of refrigerant used can be suppressed, a refrigeration air conditioner that is compact and highly environmentally friendly can be provided.

In addition, the number of stacked flat tubes (the number of parallel channels by each flat tube) can be changed according to the type of low-temperature fluid and high-temperature fluid, maximizing the temperature efficiency of the fluid flowing through each flat tube, Can minimize pressure loss and increase heat exchange performance. Further, it is possible to suppress an increase in power of the driving device for sending and circulating the fluid to the heat exchanger.

Further, in the first flat tube and the second flat tube, the temperature efficiency of the fluid flowing through each through hole is maximized by changing at least one of the number of through holes, the flow path cross-sectional area, and the arrangement pitch P. And pressure loss can be minimized, and heat exchange performance can be increased. Further, it is possible to suppress an increase in power of the driving device for sending and circulating the fluid to the heat exchanger.

Embodiment 2. FIG.
6 (a) is a view showing a heat exchanger 10 according to Embodiment 2 of the present invention, FIG. 6 (a) is a side view seen from the same direction as FIG. 1 (b), and FIG. It is sectional drawing in the bb line of Fig.6 (a).
In the figure, at least one of the first inlet header 3, the first outlet header 4, the second inlet header 5 (not shown), and the second outlet header 6 (not shown) is a pipe having both ends opened. A tubular header having a shape (in FIG. 6, all headers are tubular headers). As shown in FIG. 6 (b), the ends of the plurality of flat tubes 1a, 1b, 1c are curved in an arc shape, and are annularly formed. The inner wall 50 is formed at the center of the open end.
The tube end of the flat tube may be flush with the inner wall as viewed from the inside of the tubular header, or may be connected by protruding or retracting.
In addition, an orifice 51 having a channel cross-sectional area smaller than the front and rear channel cross-sectional areas is provided between both open ends of the first inlet header 3, that is, inside the first inlet header 3. Other configurations are the same as those in the first embodiment, and thus description thereof is omitted.

According to such a configuration, in addition to achieving uniform flow resistance to the through hole of each flat tube, the flow resistance difference to each through hole is relatively small due to the flow resistance of the orifice 51, The refrigerant is more easily distributed evenly. Therefore, the temperature efficiency of the fluid can be maximized, the pressure loss can be minimized, and the heat exchange performance can be further increased.
The same effect can be obtained if the orifice 51 is provided not only in the first inlet header 3 but also in other headers.

Further, the ends of the curved flat tubes connected to the tubular header outlet may be configured so as to overlap each other so as to partially overlap each other as shown in FIG. In this case, the diameter of the tubular header can be reduced and the size becomes more compact.
In FIG. 7, the first flat tubes 1a and 1b are composed of two, but the number may be one or three or more.

FIG. 8 shows a tubular header formed by drawing or pressing from a straight pipe. FIG. 8A is a perspective view of the first inlet header 3 viewed from the outlet side, and FIG. 8 (a) is a rear view as viewed from the direction of arrow b, FIG. 8 (c) is a cross-sectional view taken along the line cc of FIG. 8 (b), and FIG. 8 (d) is a front view as viewed from the direction of arrow d in FIG. FIG.
The tubular header shown in FIG. 8 has, at one end, the outer periphery of the tube is deformed in the radial direction to provide openings 52a, 52b, 52c to which the flat tube is connected, and the inner wall 50 is formed by joining the central portions. Yes.
By configuring the tubular header in this way, the header structure can be simplified, and the header structure can be further compacted, and the manufacturing process can be greatly simplified.

FIG. 9 shows an integral molding of the orifice 51 provided inside the tubular header, and can further improve the fluid distribution characteristics to the through-holes of each flat tube at low cost.
In FIG. 9, a flat tube is connected to the left open end.

When the gas-liquid two-phase refrigerant flows into the second inlet header 5, the same effect can be obtained in the second inlet header 5.

The heat exchanger according to the second embodiment can be used for all the refrigeration air conditioners shown in FIG. 2, FIG. 4, and FIG. When a low-temperature fluid in a gas-liquid two-phase state flows into the first inlet header 3, as shown in FIG. 6B, the fluid that has flowed into the first inlet header 3 enters the inner wall 50 at the center of the outlet end of the header. Mixing of gas and liquid is promoted by collision, and it spreads in the radial direction and flows into the annularly arranged through holes, so that the gas-liquid ratio of the fluid flowing to each through hole is more evenly distributed regardless of the operating conditions and posture I can.
Moreover, since the fluid can be accelerated by the orifice 51 and collided with the center portion,
During acceleration and collision, mixing of gas and liquid is further promoted, and even distribution to each through-hole can be increased, so that the temperature efficiency of the fluid can be maximized and the pressure loss can be minimized. The performance of the heat exchanger can be increased.

Embodiment 3 FIG.
10 is a view showing a heat exchanger 10 according to Embodiment 3 of the present invention, FIG. 10 (a) is a front view, and FIG. 10 (b) is a sectional view taken along line bb of FIG. 10 (a). FIG. 10 (c) shows FIG. 10 (a).
It is sectional drawing in the cc line.
In the figure, each of the first flat tube 1 and the second flat tube 2 has a plurality of through-holes through which a low-temperature fluid and a high-temperature fluid flow. The fluid flow directions (L1 direction and L2 direction) on the surface where the first flat tube and the second flat tube are in contact with each other are alternately stacked and joined by brazing or the like.
The first flat tube 1 is composed of six flat tubes 1a, 1b, 1c, 1d, 1e, and 1f.
a, 1b, 1c and the flat tubes 1d, 1e, 1f are respectively flat tubes 1 along flat surfaces.
In the width direction (direction perpendicular to the flow direction: W1 direction). Also, the flat tubes 1a and 1b
, 1c and the flat tubes 1d, 1e, 1f are arranged side by side in the stacking direction (S direction). Moreover, the upper and lower ends of each flat tube 1a, 1b, 1c, 1d, 1e, 1f are connected to the 1st inlet header pipe | tube 3 and the 1st outlet header 4, and comprise a parallel flow path.
The second flat tube 2 is folded in the longitudinal direction (L2 direction) and laminated in three stages, and both ends are second
The inlet header 5 and the second outlet header 6 are connected.

The total flow area of the first flat tube 1 is larger than the total flow area of the second flat tube 2.
The length of the first flat tube in the longitudinal direction (L1 direction) is the same as the length of the second flat tube (L2 direction).
The length is shorter than.
In FIG. 10, the flow passage cross-sectional areas or the numbers of the through holes of the six first flat tubes are all the same, but the flat tubes in contact with the outlet side of the second flat tubes 2 The channel cross-sectional area or number may be increased.
Similarly, the cross-sectional area or number of the through holes of the second flat tube 2 may be increased toward the side in contact with the inlet side of the first flat tube 1.

Further, as shown in FIG. 10C, the first inlet header 3 is the tubular header shown in the first embodiment or the second embodiment. First outlet header 4, second inlet header 5
The second outlet header 6 is a header that connects each flat tube to the header side surface so that the tube axis direction and the flat surface of the flat tube are parallel to each other.
Furthermore, each header 3-6 is connected with connection piping 3a, 4a, 5a, 6a, respectively.

The material of the first flat tube 1 and the second flat tube 2 is 1000 such as A1050 and A1070.
Aluminum alloy such as the number stand, 3000 series such as A3003, and 6000 series, the material of each header 3-6 is steel such as stainless steel and carbon steel, and the material of the connecting pipes 3a-6a is made of copper and copper alloy These are joined by brazing or the like.

Moreover, in this Embodiment, the 1st inlet header 3 is installed so that the pipe-axis direction A may become a perpendicular direction.

In FIG. 10, FC indicates the flow of the low temperature fluid, and FH indicates the flow of the high temperature fluid. The low-temperature fluid flows in the order of the first inlet header 3, the first flat tube 1, and the first outlet header 4, and the high-temperature fluid flows in the order of the second inlet header 5, the second flat tube 2, and the second outlet header 6. Both fluids exchange heat through the contact surface between the tube 1 and the second flat tube 2.

In order to increase the heat exchange performance, it is necessary to increase the contact area.
Since the first flat tube and the second flat tube are stacked and arranged so that the flow directions of the respective fluids are orthogonal to each other, the first flat tube and the second flat tube are not increased in size two-dimensionally. The contact area can be increased. In addition, since the flow directions of the fluids are configured to be orthogonal, the headers connected to the flat tubes do not interfere with each other. Simplification of processing when joining flat tubes and headers can be achieved.

In the present embodiment, the first flat tube and the second flat tube are stacked and arranged so that the flow directions of the respective fluids are orthogonal to each other. Therefore, the first header and the second flat tube connected to the first flat tube are arranged. Since there is no interference with the second header connected to the tube, a plurality of flat tubes can be laminated in the laminating direction to increase the contact area. As a result, the heat exchange performance can be improved, and the heat exchanger becomes compact without being two-dimensionally enlarged.
In addition, since the width or length of the first flat tube and the width or length of the second flat tube can be made different, the length and width of the flat tube are changed according to the types of the low temperature fluid and the high temperature fluid. The temperature efficiency of each fluid can be maximized, and the pressure loss can be minimized, the heat exchange performance can be increased, and the increase in power of the drive device for sending and circulating the fluid to the heat exchanger can be suppressed.

Furthermore, since the first flat tube or the second flat tube is composed of a plurality of flat tubes (only the first flat tube in FIG. 10) and a parallel flow path is formed, without increasing the pressure loss. The heat exchange characteristic can be increased by increasing the fluid flow rate. Further, there is no increase in power of the driving device for sending and circulating the fluid to the heat exchanger.

Further, either the inlet header or the outlet header connected to the flat tubes constituting the parallel flow path is a tubular header (only the first inlet header in FIG. 10), and a plurality of flat tubes constituting the parallel flow path are bundled. In addition, since the pipe axis direction of the tubular header and the flow direction of the fluid in the plurality of flat pipes constituting the parallel flow path are connected to the opening end of the tubular header, Since the through holes of the pipe are arranged almost evenly with respect to the fluid flowing in or out from the other open end of the tubular header, the flow resistance difference with respect to each through hole is small, and the fluid is evenly distributed or mixed. Therefore, the flow rate in each flat tube can be made uniform, and the heat exchange performance is improved.

Furthermore, since a plurality of flat tubes arranged along a flat surface are relatively close to each other and their ends, when connecting to a tubular header, the ends of the flat tubes are made flat. In addition to bending along the stacking direction, the pipes for bundling the ends of the flat tubes in one place can be easily routed, and the entire heat exchanger can be made compact.
In addition, since the ends of the plurality of flat tubes arranged in the stacking direction are relatively close to each other, when connecting to the tubular header, the ends of the flat tubes are bent by bending the ends of the flat tubes in the stacking direction. The piping for bundling the parts in one place becomes easy, and the entire heat exchanger can be configured compactly.

Further, by providing the connection pipes 3a to 6a made of copper and copper alloy, the attachment with the external copper pipe is further facilitated.

Although a tubular header is applied to the first inlet header 3 in the present embodiment, a tubular header may be applied to the first outlet header 4.
Moreover, in this Embodiment, although the heat exchanger by which five layers were laminated | stacked in the lamination direction by the six 1st flat tubes 1 and the 1st 2nd flat tube 2 folded and comprised was shown, the lamination direction The number of the first flat tubes arranged in line and the number of the first flat tubes arranged along the flat surface are not limited to those in the present embodiment.
Moreover, a parallel flow path may be constituted by a plurality of first flat tubes arranged only in the laminating direction, or a parallel flow path is constituted only by a plurality of first flat tubes arranged along a flat surface. The plurality of first flat tubes arranged along the line may be folded back in the stacking direction.
Further, the second flat tube 2 has the same configuration as the first flat tube, and both the first flat tube and the second flat tube are arranged along a flat surface or arranged in the stacking direction. It is good also as a parallel flow path.
When the 2nd flat tube 2 is used as a parallel flow path, it is good to make the 2nd inlet header 5 or the 2nd outlet header 6 into a tubular header like the 1st flat tube 1. FIG.

Moreover, although the case where the through-holes of the first flat tube 1 and the second flat tube 2 are arranged in a row is shown here, the through-holes need not be in a row, and may be in a plurality of rows.
Moreover, although the shape of the through hole is rectangular, it may be circular, and the heat transfer area can be increased by forming protrusions on the inner surface to further improve the heat exchange characteristics.

In the present embodiment, the same tubular header as that of the first embodiment is applied to the first inlet header. However, as in the second embodiment, the ends of a plurality of flat tubes constituting the parallel flow path are formed in an arc shape. It may be curved and arranged in an annular manner or overlapping each other and connected to the open end of the tubular header.

The heat exchanger according to the third embodiment can be used for all the refrigeration air conditioners shown in FIG. 2, FIG. 4, and FIG. In the heat exchanger 10, if the first flat tube and the second flat tube have the same shape, the pressure loss when the low-temperature gas-liquid two-phase refrigerant containing the refrigerant flows through the first flat tube is In the present embodiment, the first flat tube having the parallel flow path configuration is disconnected from the second flat tube by the entire flow path, although the pressure loss when the high-temperature and high-pressure supercritical refrigerant flows through the second flat tube is larger. As the area is getting bigger,
An appropriate pressure loss can be maintained because the flow velocity in the tube can be suppressed. Moreover, since the length of the 1st flat tube in the longitudinal direction (L1 direction) is shorter than the length of the 2nd flat tube in the longitudinal direction (L2 direction), the pressure loss of the 1st flat tube can be maintained appropriately.

Furthermore, as shown in FIG. 3, since the temperature of the high-temperature refrigerant in the second flat tube is lower on the outlet side and the temperature change is small, the region where the temperature difference with the low-temperature refrigerant flowing through the first flat tube is small increases and heat is increased. Although the exchange performance is reduced, if the heat exchanger of the present embodiment is used, each of the first flat tubes 1a, 1b, 1c and the first flat tubes 1d, 1e, 1f arranged along the flat surface are penetrated. The channel cross-sectional area or number of the holes is increased as the flat tube in contact with the outlet side of the second flat tube 2, and the flat tube in contact with the outlet side of the second flat tube 2 is configured to flow more low-temperature refrigerant. Therefore, it is possible to prevent the above-described deterioration in heat exchange characteristics.
Moreover, if the heat exchanger of this Embodiment is used, the flow-path cross-sectional area or number of the through-hole of the 2nd flat tube 2 will be enlarged, and the flat tube which contacts the inlet side of the 1st flat tube 1 will increase. Since the flat tube that contacts the inlet side of the one flat tube 1 can be configured such that a higher amount of high-temperature refrigerant flows, the first flat tube having a higher cooling performance can be used for a larger flow rate of the high-temperature refrigerant flowing through the second flat tube 2. Since heat can be exchanged with the low-temperature refrigerant flowing on the inlet side of 1, the heat exchange performance can be improved.

In this way, even if there is a difference in the thermal properties such as specific heat and density and flow rate conditions between the high-temperature fluid and the low-temperature fluid, the heat exchange performance without causing an increase in pressure loss due to an increase in the flow velocity in the pipe Can be raised.

Embodiment 4 FIG.
11 is a view showing a heat exchanger 10 according to Embodiment 4 of the present invention, FIG. 11 (a) is a perspective view, and FIG. 11 (b) is a cross-sectional view taken along the line bb of FIG. 11 (a). It is.
In the figure, each of the first flat tube 1 and the second flat tube 2 has a plurality of through-holes through which a low-temperature fluid and a high-temperature fluid flow. It joins by brazing etc. so that the flow direction (L direction) of each fluid in the surface which a 1 flat tube and a 2nd flat tube contact may become parallel.
Further, if each flat tube is made of a relatively ductile material such as aluminum alloy, copper and copper alloy, or a thin flexible member, the first flat tube 1 and the second flat tube 2 are both A structure in which the longitudinal direction (L direction) is aligned and is joined in parallel with a flat surface, and the header is connected to both ends, so that it can be folded freely with respect to the direction orthogonal to the longitudinal direction (L direction). It has become. In FIG. 11, it is the structure which laminated | stacked the 1st flat tube and the 2nd flat tube by folding the 1st flat tube and the 2nd flat tube in three steps (stacking direction: S direction), and the 1st flat tube Both ends of 1 are connected to the first inlet header 3 and the first outlet header 4, respectively, and both ends of the second flat tube 2 are connected to the second inlet header 5 and the second outlet header 6, respectively.
The first flat tube 1 is composed of three flat tubes 1a, 1b, 1c arranged along the flat surface,
Configure parallel flow paths.
The first inlet header 3 is the tubular header shown in the first and second embodiments. The first outlet header 4, the second inlet header 5, and the second outlet header 6 are headers that connect each flat tube to the side of the header so that the tube axis direction and the flat surface of the flat tube are parallel to each other. is there.
Other configurations are the same as those in the third embodiment, and thus description thereof is omitted.

In order to increase the heat exchange performance, it is necessary to increase the contact area.
Since the first flat tube and the second flat tube are arranged so that the flow directions of the fluids are parallel to each other, and the flat tubes are folded and stacked, the heat exchanger does not increase in size two-dimensionally. The contact area between the first flat tube and the second flat tube can be increased.
Moreover, since the 1st header connected to a 1st flat tube and the 2nd header connected to a 2nd flat tube should just be provided only in the both ends of each flat tube, headers may interfere. Absent.
Moreover, since the flow directions of the low-temperature fluid and the high-temperature fluid can be opposed to each other, the temperature efficiency is increased and the heat exchange performance can be increased.
In addition, since at least one of the first flat tube and the second flat tube (only the first flat tube in FIG. 11) constitutes a parallel flow path by a plurality of flat tubes arranged along the flat surface, The heat exchange characteristics can be increased by increasing the fluid flow rate without increasing the pressure loss.
Further, there is no increase in power of the driving device for sending and circulating the fluid to the heat exchanger.
In addition, since either the inlet header or the outlet header connected to the flat tubes constituting the parallel flow path is a tubular header (only the first inlet header in FIG. 11), the same effect as in the third embodiment is obtained.

Note that the number of stages in which the flat tube is folded back is not limited to three, and may be any number beyond the one-stage structure in which the flat pipe is not folded back, and can be freely configured according to the mounting space of the apparatus.

The heat exchanger according to the fourth embodiment can be used for all the refrigeration air conditioners shown in FIG. 2, FIG. 4, and FIG.
The heat exchanger according to the present embodiment can be bent freely in the laminating direction with a relatively small rigidity, for example, so that when mounted in an outdoor unit of a refrigeration air conditioner, a shell of containers such as a compressor It can be arranged along the circumference, or can be arranged in a gap space between the container and the pipe, so that the mounting efficiency to the apparatus is improved and the entire apparatus is reduced in size.

Embodiment 5 FIG.
12 is a view showing a heat exchanger 10 according to Embodiment 5 of the present invention. FIG. 12 (a) is a front view, and FIG. 12 (b) is a cross-sectional view taken along line bb of FIG. 12 (a). FIG. 12 (c) shows FIG. 12 (a).
It is sectional drawing in the cc line.
In the figure, a first flat tube 1 and a second flat tube 2 each have a plurality of through holes through which a low-temperature fluid and a high-temperature fluid flow, and fluids that flow through each tube so as to contact each other on a flat surface. A plurality of stacks of 3 or more (L1 direction, L2 direction)
In FIG. 12, the layers are alternately laminated in 6) and joined by brazing or the like.
The first flat tube 1 includes three flat tubes 1a, 1b, and 1c. The flat tubes 1a, 1b, and 1c are arranged side by side in the stacking direction (S direction), and the upper and lower ends of each flat tube are first inlets. Connected to the header pipe 3 and the first outlet header 4 to form a parallel flow path.
The second flat tube 2 is folded in the longitudinal direction (L2 direction) and laminated in three stages, and both ends are second
The inlet header 5 and the second outlet header 6 are connected.

Furthermore, as shown in FIG. 12 (c), the first inlet header 3 and the first outlet header 4 have a plurality of first flats such that the tube axis direction and the flat surface of the flat tube are parallel to each other. Tube 1a, 1b
, 1c is a header connecting the header side surface. The second inlet header 5 and the second outlet header 6 are headers that connect the second flat tube 2 to the header side surface so that the tube axis direction and the flat surface of the flat tube are parallel to each other.
Each header is connected to connection piping 3a, 4a, 5a, 6a, respectively.

The length of the first flat tube in the longitudinal direction (L1 direction) is the same as the length of the second flat tube (L2 direction).
The width direction of the first flat tube 1 (direction perpendicular to the flow direction: W1 direction)
Is longer than the length of the second flat tube in the width direction (direction perpendicular to the flow direction: W2 direction).
In FIG. 12, the flow passage cross-sectional areas or the numbers of the through holes of the three first flat tubes are all the same, but the flat tube in contact with the outlet side of the second flat tube 2 is the flow passage of the through holes. The cross-sectional area or number may be increased.
Similarly, the cross-sectional area or number of the through holes of the second flat tube 2 may be increased toward the side in contact with the inlet side of the first flat tube 1.

Moreover, although the case where the through-holes of the first flat tube 1 and the second flat tube 2 are arranged in a row is shown here, the through-holes need not be in a row, and may be in a plurality of rows.
Moreover, although the shape of the through hole is rectangular, it may be circular, and the heat transfer area can be increased by forming protrusions on the inner surface to further improve the heat exchange characteristics.

The material of the first flat tube 1 and the second flat tube 2 is 1000 such as A1050 and A1070.
Aluminum alloy such as the number stand, 3000 series such as A3003, and 6000 series, the material of each header 3-6 is steel such as stainless steel and carbon steel, and the material of the connecting pipes 3a-6a is made of copper and copper alloy These are joined by brazing or the like.

In addition, in this Embodiment, although what was comprised by the three 1st flat tubes 1 laminated | stacked on the S direction and the 1st 2nd flat tube 2 folded and laminated, each flat tube was shown. The number of is not limited to the number of the present embodiment. Moreover, you may make it comprise a parallel flow path with the some flat tube arranged along the flat surface. Also, a plurality of flat tubes arranged along the flat surface may be folded back and stacked.

In the figure, FC indicates the flow of the low temperature fluid, and FH indicates the flow of the high temperature fluid. The low-temperature fluid flows in the order of the first inlet header 3, the first flat tube 1, and the first outlet header 4, and the high-temperature fluid flows in the order of the second inlet header 5, the second flat tube 2, and the second outlet header 6. Both fluids exchange heat through the contact portion between the tube and the second flat tube.

In order to increase the heat exchange performance, it is necessary to increase the contact area.
Since the first flat tube and the second flat tube are alternately arranged in six layers so that the flow directions of the respective fluids are orthogonal to each other, the first flat tube and the second flat tube are not increased in size two-dimensionally. 2 The contact area with the flat tube can be increased. In addition, since the flow directions of the fluids are configured to be orthogonal, the headers connected to the flat tubes do not interfere with each other. Simplification of processing when joining flat tubes and headers can be achieved.

In the present embodiment, the first flat tube and the second flat tube are stacked so that the flow directions of the respective fluids are orthogonal to each other. Therefore, the width or length of the first flat tube and the second flat tube Since the width or length can be configured differently, the length and width of the flat tube can be changed according to the type of low temperature fluid and high temperature fluid to maximize the temperature efficiency of each fluid and to minimize the pressure loss It is possible to suppress the increase in the heat exchange performance and the increase in the power of the drive device for sending and circulating the fluid to the heat exchanger.

Furthermore, since the first flat tube or the second flat tube is composed of a plurality of flat tubes (only the first flat tube in FIG. 12) and the parallel flow path is formed, without increasing the pressure loss. The heat exchange characteristic can be increased by increasing the fluid flow rate. Further, there is no increase in power of the driving device for sending and circulating the fluid to the heat exchanger.

Furthermore, to increase the heat exchange performance by increasing the flow rate, in order to suppress the pressure loss,
It is necessary to enlarge the inner diameter of the header so as to achieve an appropriate flow rate, and in order to maintain pressure resistance, the wall thickness increases and the outer diameter increases remarkably, but the header is made of high-strength steel, so the outer The increase in diameter can be suppressed, and it is effective for downsizing the entire heat exchanger

In addition, steel such as stainless steel and carbon steel that make up the header can be brazed and joined to aluminum alloys, copper, and copper alloys without generating weakly fragile compound layers. 10 can be attached to copper pipes generally used in home air conditioners and commercial air conditioners by brazing or the like.
Further, by providing the connection pipes 3a to 6a made of copper and copper alloy, the attachment with the external copper pipe is further facilitated.

Furthermore, since the flat tube is made of an aluminum alloy, it can be attached to the header relatively easily by brazing or the like, and the aluminum alloy can be manufactured by extrusion molding at a relatively low cost. Can be suppressed.
In addition, the relatively high-strength aluminum alloys in the 3000s and 6000s can be made thinner, so that the size and cost can be reduced.

The heat exchanger according to the fifth embodiment can be used for all the refrigeration air conditioners shown in FIGS. For refrigeration and air conditioning equipment using carbon dioxide as a refrigerant, when the high-temperature fluid flowing through the second flat tube of the heat exchanger is a high-temperature and high-pressure supercritical fluid and the low-temperature fluid flowing through the first flat tube is a gas-liquid two-phase fluid If the first flat tube and the second flat tube have the same shape, the pressure loss when the low-temperature gas-liquid two-phase refrigerant containing the refrigerant flows through the first flat tube is high temperature and high pressure supercritical. However, in this embodiment, the first flat tube has a larger width than the second flat tube and forms a parallel flow path, so that the flow velocity in the tube is larger than the pressure loss when the refrigerant in the state flows through the second flat tube. In addition, since the length is short, an appropriate pressure loss can be maintained.

Further, as shown in FIG. 12 (c), the first flat tubes 1a, 1b, 1c are vertically arranged, and the first inlet header 3 is provided on the upper portion. Even when refrigerant flows in, a liquid surface is easily formed in the header by gravity separation, and the bottom surface in the header (
The entrance to the flat tube is in the entire liquid phase, so that the fluid flows into the three first flat tubes 1a, 1b, 1c.
The temperature efficiency of the fluid can be maximized, the pressure loss can be minimized, and the performance of the heat exchanger can be increased.

Furthermore, as shown in FIG. 3, since the temperature of the high-temperature refrigerant in the second flat tube is lower on the outlet side and the temperature change is small, the region where the temperature difference with the low-temperature refrigerant flowing through the first flat tube is small increases and heat is increased. Although the exchange performance deteriorates, if the heat exchanger of the present embodiment is used, the cross-sectional area or number of the through holes of the first flat tubes 1a, 1b, and 1c arranged in the stacking direction is determined as the second flat tube. The flat tube in contact with the 2 outlet side is enlarged (in FIG. 12, the flat tube 1a> the flat tube 1b> the flat tube 1c).
Since the flat tube that contacts the outlet side of the flat tube 2 can be configured such that more low-temperature refrigerant flows, it is possible to prevent the above-described deterioration in heat exchange characteristics.
Moreover, if the heat exchanger of this Embodiment is used, the flow-path cross-sectional area or number of the through-hole of the 2nd flat tube 2 will be enlarged, and the 1st flat tube 1 will contact the inlet side, and the 1 Since it can be constituted so that the high-temperature refrigerant flows more in the through hole that comes into contact with the inlet side of the 1 flat tube 1, the first flat tube having a high cooling performance is used for the flow rate of the high-temperature refrigerant flowing through the second flat tube 2. Since heat can be exchanged with the low-temperature refrigerant flowing on the inlet side of 1, the heat exchange performance can be improved.

In this way, even if there is a difference in the thermophysical values such as specific heat and density and operating conditions such as flow conditions between the two fluids, there is no increase in pressure loss due to an increase in the flow velocity in the pipe, Width Length,
Since the heat exchanger can be optimally configured by adjusting the number of stacked layers and the cross-sectional area and the number of through holes, it is possible to maximize the performance of the heat exchanger and thus improve the performance of the equipment.
In addition, since the heat exchanger can be configured in a compact manner and an increase in the amount of refrigerant used can be suppressed, a refrigeration air conditioner that is compact and highly environmentally friendly can be provided.

Embodiment 6 FIG.
13 is a view showing a heat exchanger according to Embodiment 6 of the present invention. FIG. 13 (a) is a perspective view, and FIG. 13 (b) is a cross-sectional view taken along line bb in FIG. 13 (a). is there.
In the figure, each of the first flat tube 1 and the second flat tube 2 has a plurality of through-holes through which a low-temperature fluid and a high-temperature fluid flow. It joins by brazing etc. so that the flow direction (L direction) of each fluid in the surface which a 1 flat tube and a 2nd flat tube contact may become parallel.
Further, if each flat tube is made of a relatively ductile material such as aluminum alloy, copper and copper alloy, or a thin flexible member, the first flat tube 1 and the second flat tube 2 are both A structure in which the longitudinal direction (L direction) is aligned and is joined in parallel with a flat surface, and the header is connected to both ends, so that it can be folded freely with respect to the direction orthogonal to the longitudinal direction (L direction). It has become. FIG. 13 shows a configuration in which six layers of the first flat tube and the second flat tube are stacked in the stacking direction by folding the first flat tube and the second flat tube in three stages (stacking direction: S direction). Both ends of the first flat tube 1 are connected to the first inlet header 3 and the first outlet header 4, respectively, and both ends of the second flat tube 2 are connected to the second inlet header 5 and the second outlet header 6, respectively.
The first inlet header 3, the first outlet header 4, the second inlet header 5, and the second outlet header 6 are arranged so that the tube axis direction and the flat surface of the flat tube are parallel to each other. Is a header that connects to the side of the header.

In order to increase the heat exchange performance, it is necessary to increase the contact area.
Since the first flat tube and the second flat tube are arranged so that the flow directions of the fluids are parallel to each other, and the flat tubes are folded and stacked, the heat exchanger does not increase in size two-dimensionally. The contact area between the first flat tube and the second flat tube can be increased.
Moreover, since the 1st header connected to a 1st flat tube and the 2nd header connected to a 2nd flat tube should just be provided only in the both ends of each flat tube, headers may interfere. Absent.
Moreover, since the flow directions of the low-temperature fluid and the high-temperature fluid can be opposed to each other, the temperature efficiency is increased and the heat exchange performance can be increased.

In addition, it cannot be overemphasized that it is the same effect | action and effect even if it arranges and arranges the thin tube which has a through hole instead of a flat tube.

In addition, the heat exchanger of this Embodiment 6 can be utilized for all the refrigeration air conditioners shown in FIG.2, FIG.4, FIG.5.
When a low-temperature fluid in a gas-liquid two-phase state flows into the first header inlet 3, it is desirable to arrange the flow in the first flat tube so as to be vertically downward. In this case, in the first inlet header by gravity separation The liquid level is easily formed on the first flat tube, and the refrigerant is easily distributed equally to each of the through holes of the first flat tube.

Moreover, since the heat exchanger of this Embodiment can be freely bent to the lamination direction where the longitudinal direction is comparatively small, for example, when mounted on the outdoor unit of the refrigeration air conditioner,
For example, it can be disposed along a compressor, a reservoir, or the like, or in a gap space between the container and the piping, so that the mounting efficiency to the apparatus is improved and the entire apparatus is reduced in size.

Note that the number of stages in which the flat tube is folded back is not limited to three, and may be any number beyond the one-stage structure in which the flat pipe is not folded back, and can be freely configured according to the mounting space of the apparatus.

Embodiment 7 FIG.
14 is a view showing a heat exchanger according to Embodiment 7 of the present invention, in which FIG. 14 (a) is a perspective view, FIG. 14 (b) is a cross-sectional view in the xz plane, and FIG. 14 (c) is an xy plane. FIG.
In the figure, each of the first flat tube 1 and the second flat tube 2 has a plurality of through-holes through which a low-temperature fluid and a high-temperature fluid flow, and the longitudinal direction (surface where the first flat tube and the second flat tube are in contact with each other) Are integrally formed so that the flow directions of the fluids in FIG. The integrally formed first flat tube 1 and second flat tube 2 are made of a relatively ductile material such as aluminum alloy, copper and copper alloy, or a thin flexible member. Bend at 3
It is composed of stages. Further, at both ends of the integrally formed first flat tube 1 and second flat tube 2,
The tubular member is connected so that the flat surface of the flat tube and the tube axis direction are parallel to each other. By inserting a partition plate 52 in the longitudinal direction inside the tubular member, the first inlet header 3 and Second
The outlet header 6 is disposed adjacently via the partition plate 52, and the first outlet header 4 and the second inlet header 5 are disposed adjacently via the partition plate 52. The first inlet header 3 and the first outlet header 4 are connected at both ends, and the second inlet header 5 and the second outlet header 6 are connected at both ends of the second flat tube 2.
The tube in which the flow path of the first flat tube and the flow path of the second flat tube are integrated can be processed by, for example, aluminum extrusion.

According to such a configuration, in addition to the effects of the sixth embodiment, the contact thermal resistance between the first flat tube 1 and the second flat tube 2 can be completely eliminated, and the heat exchange performance can be greatly improved. can get.
In addition, the flat tube integrated molding and header integration make it even more compact,
Manufacturing can be greatly simplified.

In addition, although the case where the through-holes of the first flat tube 1 and the second flat tube 2 are arranged in a row is shown here, the through-holes need not be in a row, and may be in a plurality of rows. .

Embodiment 8 FIG.
15 is a view showing a heat exchanger according to an eighth embodiment of the present invention. FIG. 15 (a) is a perspective view, FIG. 15 (b) is a cross-sectional view in the xz plane, and FIG. 15 (c) is a yz plane. FIG.
A porous tube 60 integrally formed by arranging three passages each having a plurality of through-holes corresponding to the first flat tube 1 and the second flat tube 2 of Embodiment 6 in a total of six steps; The first header body 61 and the second header body 62 are provided at both ends of the 60. First header body 6
1 communicates with the partition plates that divide the first to fourth, fifth, and sixth stages of the porous tube, and the flow paths of the fifth and sixth stages of the porous tube, respectively. A first outlet pipe 611 and a second inlet pipe 612 connected to each other. The second header body 62 communicates with a partition plate that divides the first stage, the second stage, and the third to sixth stages of the perforated pipe, and the first and second stage flow paths of the perforated pipe, respectively. A first inlet pipe 621 and a second outlet pipe 622 connected to each other. Also,
A first cover 613 that communicates between the second and third flow paths of the porous tube 60 built in the first header body 61, and a third and sixth stage of the porous tube 60 built in the second header body 62. A second cover 623 that communicates the flow path is provided.

With this configuration, the low-temperature fluid meanders the first header body 61, the porous pipe 60, and the second header body 62 from the first inlet pipe 621 to the first outlet pipe 611, while the high-temperature fluid However, the second header body 62, the perforated pipe 60, and the first header body 61 can meander from the second inlet pipe 612 to alternately flow to the second outlet pipe 622.

Therefore, according to such a configuration, the same effects as those of the sixth embodiment can be obtained, and in addition to that, the flat tube portion can be further integrally formed and the header can be integrated, thereby further compacting. At the same time, the manufacturing can be greatly simplified.

Note that the first header body 61 and the first cover 613, and the second header body 62 and the second cover 623 may be integrally formed, and further manufacturing can be simplified by reducing the number of parts.
Moreover, although the case of the integrally formed porous tube 60 is shown here, the porous tube may be configured by laminating the first flat tube and the second flat tube.
In addition, here, the case where the through holes constituting the flow paths of the respective stages are arranged in a row is shown, but the through holes are not necessarily arranged in a row, and may be formed in a plurality of rows.

Embodiment 9 FIG.
16 is a view showing a heat exchanger according to Embodiment 9 of the present invention, in which FIG. 16 (a) is a perspective view, FIG. 16 (b) is a cross-sectional view on the yz plane, and FIG. 16 (c) is a porous tube. FIG.
A porous tube 60 integrally formed by arranging three stages of flow passages each having a plurality of through holes corresponding to the first flat tube 1 and the second flat tube 2 of the sixth embodiment, a total of six steps; The first header body 61 and the second header body 62 are provided at both ends of the tube 60.

The first header body 61 and the second header body 62 include a first outlet pipe 611 and a first inlet pipe 621 respectively connected to communicate with the second, fourth, and sixth stage flow paths of the porous pipe 60. ing.
Further, it is built in the first header body 61 and the second header body 62,
The first internal header 631 and the second internal header 632 are respectively connected so as to communicate with the fifth-stage flow path. Further, the first internal header 631 and the second internal header 632 are respectively supplied with high-temperature fluid from the outside. A second inlet pipe 612 and a second outlet pipe 622 are connected to each other.

With this configuration, the low-temperature fluid is transferred from the first inlet pipe 621 to the first header body 61, the porous pipe 60, the second header body 62, and the first outlet pipe 611, while the high-temperature fluid is supplied to the second header pipe 61, the porous pipe 60, the second header body 62, and the first outlet pipe 611.
From the inlet pipe 612, the second header body 62, the porous pipe 60, the first header body 61, and the second outlet pipe 622 can be alternately opposed to flow.
Moreover, although the case of the integrally formed porous tube is shown here, the porous tube may be configured by laminating the first flat tube and the second flat tube.

Therefore, according to such a configuration, the same effects as those of the sixth embodiment can be obtained, and in addition to this, the header structure can be simplified, the size can be further reduced, and the manufacturing can be greatly simplified. be able to.

As shown in FIG. 16 (c), since the end of the porous tube 60 has an uneven structure, the flow of the high-temperature fluid and the low-temperature fluid flows by joining the header body, the internal header, and the porous tube. The path can be formed relatively easily.

Embodiment 10 FIG.
17 is a view showing a heat exchanger according to Embodiment 10 of the present invention, in which FIG. 17 (a) is a perspective view and FIG. 17 (b) is a cross-sectional view in the xy plane.
Each of the first flat tube 1 and the second flat tube 2 has a plurality of through holes through which a low-temperature fluid and a high-temperature fluid flow. The first flat tube 1 and the second flat tube 2 are in contact with each other on a flat surface and in the longitudinal direction (first flat tube). The flow direction of each fluid on the surface where the second flat tube and the second flat tube contact each other (L direction)
They are stacked alternately and joined by brazing or the like.
The first flat tube 1 includes three first flat tubes 1a, 1b, 1c, and second arranged in the stacking direction (S direction).
The flat tube 2 is composed of three second flat tubes 2a, 2b, 2c arranged in the stacking direction (S direction), and both ends of the first flat tubes 1a, 1b, 1c and both ends of the second flat tubes 2a, 2b. The first flat tubes 1a, 1b, 1c and the second flat tubes 2a, 2b, 2c are bent at predetermined angles along flat surfaces so that they do not overlap when viewed from the stacking direction. That is, the first flat tubes 1a, 1b, 1
c and both ends of the second flat tubes 2a, 2b, and 2c in the direction (W direction) orthogonal to both the longitudinal direction (L direction) and the stacking direction (S direction), respectively. The both ends of the 1 flat tube 1 and the 2nd flat tube 2 are bent so that they may not cross each other.
The first flat tubes 1a, 1b, and 1c are connected to the first inlet header 3 and the first outlet header 4 at both ends, respectively, and constitute a parallel flow path.
Further, the second flat tubes 2a, 2b, 2c are connected to the second inlet header 5 and the second outlet header 6 at both ends, respectively, to constitute a parallel flow path.
Furthermore, the flow passage cross-sectional area (cross-sectional area perpendicular to the fluid flow direction) or number of the through hole of the first flat tube 1 is configured to be larger than that of the second flat tube 2, and the total flow area of the first flat tube 1 is It is larger than the second flat tube.

The first inlet header 3, the first outlet header 4, the second inlet header 5, and the second outlet header 6 have branch branches whose tube axes are orthogonal to the flat surfaces of a plurality of flat tubes that form parallel flow paths. The plurality of flat tubes are connected to a side surface of the branch branch header.

The material of the first flat tube 1 and the second flat tube 2 is 1000 such as A1050 and A1070.
The material of the base, aluminum alloys such as 3000 series such as A3003, and 6000 series, and steels such as stainless steel and carbon steel are joined by brazing or the like.

According to the configuration of the present embodiment, both ends of the first flat tube or both ends of the second flat tube are arranged so that both ends of the first flat tube and both ends of the second flat tube do not overlap when viewed from the stacking direction. Since the first flat tube and the second flat tube are alternately laminated so that the flow directions thereof are parallel, the first flat tube connected to the first flat tube is configured by bending along a flat surface. Since the first header and the second header connected to the second flat tube do not interfere with each other, a plurality of flat tubes can be stacked in the stacking direction to increase the contact area. As a result, the heat exchange performance can be improved, and the heat exchanger becomes compact without being two-dimensionally enlarged.
Moreover, since it can be enlarged not only in the width direction but also in the stacking direction of the first flat tube and the second flat tube, without increasing the power loss of the driving device for sending and circulating the fluid to the heat exchanger due to the increase in pressure loss. In addition, the heat exchange characteristics can be increased by increasing the flow rates of the low temperature fluid and the high temperature fluid.
Further, it is possible to simplify the processing when joining the flat tube and the header by brazing at the time of manufacture.

In addition, since the first header and the second header do not interfere with each other, the plurality of first flat tubes and the plurality of second flat tubes arranged in the stacking direction can be configured to be parallel flow paths, respectively. The heat exchange characteristics can be increased by increasing the fluid flow rate without increasing the pressure loss. Further, there is no increase in power of the driving device for sending and circulating the fluid to the heat exchanger.

In addition, if the same flat tube with the same bending angle is used for both the first flat tube and the second flat tube, it can be configured by being inverted upside down, thereby further simplifying the manufacturing process and management. be able to.
Moreover, although the case where the through-holes of the first flat tube 1 and the second flat tube 2 are arranged in a row is shown here, the through-holes need not be in a row, and may be in a plurality of rows.

In addition, the heat exchanger of this Embodiment 10 can be used for all the refrigeration air conditioners shown in FIG. 2, FIG. 4, FIG.
When a low-temperature fluid in a gas-liquid two-phase state flows into the first header inlet 3, it is desirable to arrange the flow in the first flat tube so as to be vertically downward. In this case, in the first inlet header by gravity separation The liquid level is easily formed on the first flat tube, and the refrigerant is easily distributed equally to each of the through holes of the first flat tube.

In addition, the heat exchanger 10 uses the heat exchanger of Embodiment 10, and each flat tube is made of a relatively large ductile material such as an aluminum alloy, copper, and a copper alloy, or a thin flexible member. Since both the first flat tube 1 and the second flat tube 2 are aligned in the longitudinal direction (L direction) in parallel and joined by flat surfaces, and the headers are connected to both ends. Because the longitudinal direction can be bent freely in the laminating direction with relatively low rigidity, when mounted on the outdoor unit of a refrigeration air conditioner, it can be placed along the components (for example, compressors and reservoirs) , Can be placed in the gap space between the container and piping, and the mounting efficiency to the device is improved,
Contributes to downsizing of the entire device.

As described above, in the heat exchanger according to the present invention, the first flat tube and the second flat tube are stacked with a plurality of stacks of three or more so that the flow directions of the respective fluids are orthogonal to each other. , Heat exchanger
It is compact without increasing in size two-dimensionally, and can be increased not only in the width direction of the first flat tube and the second flat tube but also in the stacking direction. Heat exchange characteristics can be increased by increasing the flow rate of the fluid.
Further, since at least one of the first flat tube and the second flat tube is composed of a plurality of flat tubes arranged along the flat surface or arranged in the stacking direction, the pressure loss is increased. And the heat exchange characteristics can be increased by increasing the fluid flow rate.
In addition, either the inlet header or the outlet header connected to the flat tubes constituting the parallel flow path is a tubular header, and a plurality of flat tubes constituting the parallel flow path are bundled, and the tubular header is formed at the opening end of the tubular header. If the connection is made so that the flow direction of the fluid in the plurality of flat tubes constituting the parallel flow path is the same direction, the through hole of each flat tube at the open end is the other side of the tubular header. Since the fluid flowing in or out from the open end is arranged almost evenly, the flow resistance difference with respect to each through hole is small, and the fluid is evenly distributed or mixed, so the flow rate in each flat tube is uniform. And heat exchange performance is improved.

Further, in the heat exchanger according to the present invention, the first flat tube and the second flat tube are folded so that the flow directions of the respective fluids are parallel to each other, and are arranged in a plurality of layers of 3 or more. Since the heat exchanger becomes compact without increasing in size two-dimensionally, and can be increased not only in the width direction of the first flat tube and the second flat tube but also in the stacking direction, without causing an increase in pressure loss, The heat exchange characteristics can be increased by increasing the flow rates of the cold fluid and the hot fluid.
Further, at least one of the first flat tube and the second flat tube is constituted by a plurality of flat tubes arranged along a flat surface, and the plurality of flat tubes constitute a parallel flow path. In this case, the heat exchange characteristics can be increased by increasing the fluid flow rate without increasing the pressure loss.
In addition, either the inlet header or the outlet header connected to the flat tube constituting the parallel flow path is a tubular header, a plurality of flat tubes constituting the parallel flow path are bundled, and a tubular header is formed at the opening end of the tubular header. If the connection is made so that the pipe axial direction of the header and the flow direction of the fluid in the plurality of flat tubes constituting the parallel flow path are in the same direction, the through hole of each flat tube at the open end is the other side of the tubular header Because the fluid flows in or out from the open end of the tube, the flow resistance difference for each through hole is small and the fluid is evenly distributed or mixed, so the flow rate in each flat tube is uniform. The heat exchange performance is improved.

In the heat exchanger according to the present invention, the first flat tube and the second flat tube are stacked so that the flow directions of the respective fluids are parallel to each other, so that the heat exchanger is two-dimensionally enlarged. And the flow rate of the low-temperature fluid and the high-temperature fluid can be increased without causing an increase in pressure loss because the size can be increased not only in the width direction but also in the stacking direction of the first flat tube and the second flat tube. The heat exchange characteristics can be increased.
In addition, since at least one of the first flat tube and the second flat tube is composed of a plurality of flat tubes arranged in the stacking direction, the plurality of flat tubes constitute a parallel flow path. The heat exchange characteristics can be increased by increasing the fluid flow rate without increasing the pressure loss.
Further, both ends of the plurality of flat tubes are bent in a direction perpendicular to both the flow direction of each fluid and the stacking direction so that the both ends of the first flat tube and the both ends of the second flat tube do not intersect each other. Therefore, even if the first flat tubes and the second flat tubes are alternately stacked so that the flow directions are parallel, headers connected to both ends of each flat tube do not interfere.
In addition, either the inlet header or the outlet header connected to the flat tubes constituting the parallel flow path is a tubular header, and a plurality of flat tubes constituting the parallel flow path are bundled, and the tubular header is formed at the opening end of the tubular header. If the connection is made so that the flow direction of the fluid in the plurality of flat tubes constituting the parallel flow path is the same direction, the through hole of each flat tube at the open end is the other side of the tubular header. Since the fluid flowing in or out from the open end is arranged almost evenly, the flow resistance difference with respect to each through hole is small, and the fluid is evenly distributed or mixed, so the flow rate in each flat tube is uniform. And heat exchange performance is improved.

In addition, the heat exchanger according to the present invention includes the first flat tube or the second flat tube made of an aluminum alloy and each header made of steel, so that it can be reduced in size and cost and is generally used. There is an effect that it can be attached to a copper pipe that is relatively easy.

Moreover, since the refrigerating and air-conditioning apparatus according to the present invention uses the heat exchanger of the present invention, a high-performance and compact refrigerating and air-conditioning apparatus can be obtained.

DESCRIPTION OF SYMBOLS 1 1st flat pipe, 2 2nd flat pipe, 3 1st inlet header, 4 1st outlet header, 5
2nd inlet header, 6 2nd outlet header, 10 heat exchanger, 20 compressor, 21
Radiator, 22 decompressor, 23 cooler, 31 second decompressor, 32 bypass pipe, 3
3 Injection port, 40 Auxiliary compressor, 41 Auxiliary radiator, 42 Auxiliary decompressor, 43 Liquid reservoir, 50 Inner wall 51 Orifice, 52 Partition plate, 60 Perforated tube,
61 1st header body, 62 2nd header body, 611 1st outlet pipe, 612 2nd inlet pipe, 613 1st cover, 621 1st inlet pipe, 622 2nd outlet pipe, 623 2nd cover, 631 1st inside Header, 632 Second internal header.

Claims (11)

A flat first flat tube having a through hole through which a low temperature fluid flows, a flat second flat tube having a through hole through which a high temperature fluid flows, and a first inlet header connected to both ends of the first flat tube, respectively. And a first outlet header and a second inlet header and a second outlet header connected to both ends of the second flat tube, respectively, wherein the first flat tube and the second flat tube Are arranged so that they are in contact with each other on a flat surface and the flow direction of the low fluid and the flow direction of the high-temperature fluid are parallel to each other, and the first flat tube and the second At least one flat tube with the flat tube is composed of a plurality of flat tubes arranged in the stacking direction, and the plurality of the plurality of flat tubes are arranged so that both ends of the first flat tube and both ends of the second flat tube do not intersect each other. The flow direction of each of the fluids above both ends of the flat tube Bending along a direction perpendicular to any of the laminating directions and along the flat surface, the plurality of flat tubes and an inlet header and an outlet header respectively provided at both ends of the flat tubes A heat exchanger comprising a flow path. Either the inlet header that constitutes the parallel flow path or the outlet header that constitutes the parallel flow path is constituted by a branch-branch header whose tube axis is orthogonal to the flat surfaces of the plurality of flat tubes constituting the parallel flow path. The heat exchanger according to claim 1, wherein the plurality of flat tubes are connected to a side surface of the branch branch header. Either the inlet header constituting the parallel flow path or the outlet header constituting the parallel flow path is constituted by a tubular header having both ends opened, and the plurality of flat tubes constituting the parallel flow path are bundled to form the tubular header The heat exchanger according to claim 1, wherein a tube axial direction of the tubular header and a flow direction of fluid in the plurality of flat tubes are connected to the open end of the tubular header in the same direction. Each of the first flat tube and the second flat tube has a plurality of through holes, and the through holes of the first flat tube and the through holes of the second flat tube have a number, a channel cross-sectional area, and an arrangement pitch. The heat exchanger according to any one of claims 1 to 3, wherein at least one of them is different. The heat exchanger according to any one of claims 1 to 4, wherein at least one of the low-temperature fluid and the high-temperature fluid is a gas-liquid two-phase fluid. At least one of the low-temperature fluid and the high-temperature fluid is a gas-liquid two-phase fluid, and the flow direction in the gas-liquid two-phase state flowing in the first flat tube or the second flat tube is the vertical direction. The heat exchanger according to any one of claims 1 to 5, wherein one flat tube or a second flat tube is disposed. The plurality of flat tubes constituting the parallel flow path are arranged in an annular shape by curving the ends of the flat tubes in an arc shape,
The heat exchanger according to claim 3, wherein the heat exchanger is connected to an open end of a tubular header. The heat exchanger according to claim 3, wherein an orifice having a channel cross-sectional area smaller than the front and rear channel cross-sectional areas is provided inside the tubular header. The at least one of the low temperature fluid and the high temperature fluid is carbon dioxide.
The heat exchanger of any one of -8. The heat exchanger according to any one of claims 1 to 9, wherein the first flat tube or the second flat tube is made of an aluminum alloy, and each header is made of steel. A refrigeration air conditioner using the heat exchanger according to any one of claims 1 to 10.

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