CN116802453A - Heat exchanger and refrigeration cycle device provided with same - Google Patents
Heat exchanger and refrigeration cycle device provided with same Download PDFInfo
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- CN116802453A CN116802453A CN202180091905.2A CN202180091905A CN116802453A CN 116802453 A CN116802453 A CN 116802453A CN 202180091905 A CN202180091905 A CN 202180091905A CN 116802453 A CN116802453 A CN 116802453A
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- heat exchanger
- side portion
- flow path
- opening end
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- 238000005057 refrigeration Methods 0.000 title claims description 14
- 238000012546 transfer Methods 0.000 claims abstract description 83
- 238000013459 approach Methods 0.000 claims description 5
- 230000017525 heat dissipation Effects 0.000 claims 2
- 230000007423 decrease Effects 0.000 abstract description 10
- 239000003507 refrigerant Substances 0.000 description 66
- 238000000034 method Methods 0.000 description 15
- 238000004519 manufacturing process Methods 0.000 description 11
- 230000000694 effects Effects 0.000 description 9
- 239000007788 liquid Substances 0.000 description 8
- 239000000463 material Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 3
- 238000001125 extrusion Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/04—Arrangements for sealing elements into header boxes or end plates
- F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
- F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
- F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
- F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A flat heat transfer tube (21) of an outdoor heat exchanger (11) is provided with a main body (23) and a connection portion (25). A plurality of flow paths (27) are arranged in the flat heat transfer tube (21) at intervals. The flat heat transfer tube (21) has a 1 st side portion (29 a) and a 2 nd side portion (29 b) with a width therebetween. A connection portion (25) connected to an opening (33) of the header (31) has an opening end surface (26), and a plurality of flow paths (27) are each opened on the opening end surface (26). In the connection portion (25), the 1 st side portion (29 a) is formed in a wedge shape so that the width thereof decreases as approaching the opening end face (26). The 1 st opening end (28 a) of the 1 st flow path (27 a) closest to the 1 st side (29 a) has a 2 nd flow path cross-sectional area (S2) smaller than the 1 st flow path cross-sectional area (S1) of the opening ends (28) of the other flow paths (27).
Description
Technical Field
The present disclosure relates to a heat exchanger and a refrigeration cycle apparatus including the heat exchanger.
Background
As one form of the heat exchanger used for the air conditioner, there is a heat exchanger to which a flat heat transfer tube having a flat shape in which a plurality of flow paths through which a refrigerant flows are applied. In such a heat exchanger, in order to improve heat transfer performance during operation functioning as an evaporator, more refrigerant is required to flow into a flow path located on the windward side. For example, patent document 1 proposes a heat exchanger including a flat heat transfer tube having a larger flow path on the upstream side than a flow path on the downstream side.
Prior art literature
Patent literature
Patent document 1: japanese patent application laid-open No. 2015-90219
Disclosure of Invention
Problems to be solved by the invention
The flat heat transfer tube is manufactured by, for example, extrusion molding a material such as aluminum. In a flat heat transfer tube in which a flow path on an upstream side is larger than a flow path on a downstream side, for example, it may be difficult to manufacture a desired flat heat transfer tube due to an asymmetric cross-sectional shape. In a heat exchanger, improvement in manufacturability while ensuring heat transfer performance is demanded.
The present disclosure has been made in a loop of such development, and an object thereof is to provide a heat exchanger that achieves improvement in manufacturability while ensuring heat transfer performance, and another object is to provide a refrigeration cycle apparatus to which such a heat exchanger is applied.
Means for solving the problems
The heat exchanger of the present disclosure has flat heat transfer tubes, headers, and fins in a flat shape. The flat heat transfer tube has a 1 st side portion and a 2 nd side portion with a width in the 1 st direction, and extends in the 2 nd direction intersecting the 1 st direction. In the flat heat transfer tube, a plurality of flow paths are arranged at intervals in the 1 st direction, and each of the plurality of flow paths extends in the 2 nd direction. The header is formed with an opening portion, and the flat heat transfer tube is connected to the opening portion. The flat heat transfer tube includes a main body portion and a connection portion. The main body is attached to the heat radiating fin. The connection portion has an open end face, is inserted into the opening of the header and is connected to the header, and a plurality of flow paths are each opened at the open end face. In the main body, the plurality of flow paths each have a 1 st flow path cross-sectional area. In the connecting portion, the 1 st side portion is formed in a wedge shape so that the width thereof decreases as approaching the opening end face. On the opening end surface, the 1 st opening end of the 1 st flow path closest to the 1 st side formed in a wedge shape of the plurality of flow paths has a 2 nd flow path cross-sectional area smaller than the 1 st flow path cross-sectional area.
The refrigeration cycle device of the present disclosure is provided with the heat exchanger.
Effects of the invention
According to the heat exchanger of the present disclosure, a flat heat transfer tube includes a main body portion and a connection portion. In the flat heat transfer tube, a plurality of flow paths are arranged at intervals. The flat heat transfer tube has a 1 st side portion and a 2 nd side portion with a width therebetween. The connection portion connected to the opening portion of the header has an opening end face, and the plurality of flow paths are respectively opened at the opening end face. In the connecting portion, the 1 st side portion is formed in a wedge shape so that the width thereof decreases as approaching the opening end face. This makes it possible to easily insert the connection portion into the opening of the header, and thus to facilitate improvement in manufacturability. Further, on the opening end face, the 1 st opening end of the 1 st flow path closest to the 1 st side portion has a 2 nd flow path cross-sectional area smaller than the 1 st flow path cross-sectional area. This can allow the refrigerant to flow into the flow path in the region where the heat load is high more, and can ensure heat transfer performance.
According to the refrigeration cycle apparatus of the present disclosure, by providing the heat exchanger, manufacturability can be improved while ensuring heat transfer performance.
Drawings
Fig. 1 is a diagram showing a refrigerant circuit of a refrigeration cycle apparatus including an outdoor heat exchanger according to each embodiment.
Fig. 2 is a perspective view showing an example of the outdoor heat exchanger according to each embodiment.
Fig. 3 is a plan view including a partial cross-section, showing the structure of a portion of the outdoor heat exchanger according to embodiment 1 where the flat heat transfer tubes are connected to the header.
Fig. 4 is a sectional view taken along a section line IV-IV shown in fig. 3 in this embodiment.
Fig. 5 is a front view showing an opening end face of a connection portion of the flat heat transfer tube in this embodiment.
Fig. 6 is a diagram showing an example of a flowchart of a method for manufacturing an outdoor heat exchanger according to this embodiment.
Fig. 7 is a partial plan view showing one step of the method for manufacturing an outdoor heat exchanger according to this embodiment.
Fig. 8 is a plan view, including a partial cross section, showing a process performed after the process shown in fig. 7 in this embodiment.
Fig. 9 is a diagram for explaining the operation and effect of the outdoor heat exchanger in this embodiment.
Fig. 10 is a plan view, including a partial cross-section, showing the structure of a portion of the outdoor heat exchanger according to embodiment 2 where the flat heat transfer tubes are connected to the header.
Fig. 11 is a front view showing an opening end face of a connection portion of the flat heat transfer tube in this embodiment.
Fig. 12 is a partial plan view showing one step of the method for manufacturing an outdoor heat exchanger according to this embodiment.
Fig. 13 is a plan view including a partial cross-section, showing the structure of a portion of the outdoor heat exchanger according to embodiment 3 where the flat heat transfer tubes are connected to the header.
Fig. 14 is a front view showing an opening end face of a connection portion of the flat heat transfer tube in this embodiment.
Fig. 15 is a partial plan view showing one step of the method for manufacturing an outdoor heat exchanger according to this embodiment.
Fig. 16 is a partial plan view including a partial cross section, showing a process performed after the process shown in fig. 15 in this embodiment.
Fig. 17 is a plan view, including a partial cross-section, showing the structure of a portion of the outdoor heat exchanger according to embodiment 4 where the flat heat transfer tubes are connected to the header.
Fig. 18 is a front view showing an opening end face of a connection portion of the flat heat transfer tube in this embodiment.
Fig. 19 is a partial plan view showing one step of the method for manufacturing an outdoor heat exchanger according to this embodiment.
Fig. 20 is a perspective view showing another example of the outdoor heat exchanger according to each embodiment.
Detailed Description
First, an example of a refrigerant circuit of a refrigeration cycle apparatus including the heat exchanger (outdoor heat exchanger) of each embodiment will be described. As shown in fig. 1, the refrigeration cycle apparatus 1 includes a compressor 3, an indoor heat exchanger 5, a fan 7, an expansion valve 9, an outdoor heat exchanger 11, a propeller fan 13, a four-way valve 15, and a refrigerant pipe 17 connecting these. The configuration of the outdoor heat exchanger 11 will be described in detail in each embodiment.
Next, as the operation of the refrigeration cycle apparatus 1 described above, first, a heating operation will be described. The flow of the refrigerant during the heating operation is shown by a solid line. By driving the compressor 3, the high-temperature and high-pressure gas refrigerant is discharged from the compressor 3. The discharged high-temperature and high-pressure gas refrigerant (single-phase) flows into the indoor heat exchanger 5 through the four-way valve 15.
In the indoor heat exchanger 5, heat exchange is performed between the inflowing gas refrigerant and the air sent by the fan 7. The high-temperature and high-pressure gas refrigerant is condensed to become a high-pressure liquid refrigerant (single-phase). The heat-exchanged air is sent out from the indoor heat exchanger 5 into the room, and heats the room. The high-pressure liquid refrigerant sent from the indoor heat exchanger 5 is converted into a low-pressure gas refrigerant and a liquid refrigerant in a two-phase state by the expansion valve 9.
The refrigerant in a two-phase state flows into the outdoor heat exchanger 11. The outdoor heat exchanger 11 functions as an evaporator. In the outdoor heat exchanger 11, heat exchange is performed between the refrigerant in the two-phase state flowing in and the air supplied by the propeller fan 13. The liquid refrigerant in the two-phase refrigerant evaporates to become a low-pressure gas refrigerant (single-phase). At this time, more refrigerant flows in the refrigerant flow path on the windward side than in the refrigerant flow path on the leeward side. The low-pressure gas refrigerant is sent out from the outdoor heat exchanger 11.
The low-pressure gas refrigerant sent from the outdoor heat exchanger 11 flows into the compressor 3 through the four-way valve 15. The low-pressure gas refrigerant flowing into the compressor 3 is compressed to become a high-temperature high-pressure gas refrigerant, and is discharged from the compressor 3 again. This cycle is repeated hereinafter.
Next, a case of the cooling operation will be described. By driving the compressor 3, the high-temperature and high-pressure gas refrigerant is discharged from the compressor 3. The discharged high-temperature and high-pressure gas refrigerant (single phase) flows into the outdoor heat exchanger 11 through the four-way valve 15. The outdoor heat exchanger 11 functions as a condenser. In the outdoor heat exchanger 11, heat exchange is performed between the refrigerant flowing in and the air supplied by the propeller fan 13. The high-temperature and high-pressure gas refrigerant is condensed to become a high-pressure liquid refrigerant (single-phase).
The high-pressure liquid refrigerant sent from the outdoor heat exchanger 11 is passed through the expansion valve 9 to be a low-pressure gas refrigerant and a liquid refrigerant in a two-phase state. The refrigerant in the two-phase state flows into the indoor heat exchanger 5. In the indoor heat exchanger 5, heat exchange is performed between the refrigerant in the two-phase state flowing in and the air sent to the indoor heat exchanger 5 by the fan 7. The liquid refrigerant in the two-phase refrigerant evaporates to become a low-pressure gas refrigerant (single-phase). The heat-exchanged air is sent out from the indoor heat exchanger 5 into the room, and the room is cooled.
The low-pressure gas refrigerant sent from the indoor heat exchanger 5 flows into the compressor 3 through the four-way valve 15. The low-pressure gas refrigerant flowing into the compressor 3 is compressed to become a high-temperature high-pressure gas refrigerant, and is discharged from the compressor 3 again. This cycle is repeated hereinafter. Next, the structure of the outdoor heat exchanger 11 according to each embodiment will be described. In each embodiment, for convenience of explanation, the X-axis and the Y-axis are used for explanation.
Embodiment 1.
An example of an outdoor heat exchanger as a heat exchanger according to embodiment 1 will be described. As shown in fig. 2, an outdoor heat exchanger 11 and a header 31 are housed in a casing 10 of the outdoor unit, and the outdoor heat exchanger 11 includes flat heat transfer tubes 21 and heat radiating fins 41. Here, the single-row outdoor heat exchanger 11 is disposed. Further, the housing 10 accommodates a propeller fan 13, a compressor 3 (not shown), and the like. By driving the propeller fan 13 (not shown), air flows in the direction indicated by an arrow Y1 in the casing 10.
As shown in fig. 3, the flat heat transfer tube 21 of the outdoor heat exchanger 11 includes a main body portion 23 and a connection portion 25. The flat heat transfer tube 21 has a width in the Y-axis direction as the 1 st direction and extends in the X-axis direction as the 2 nd direction. In the flat heat transfer tube 21, a plurality of flow paths 27 each extending in the X-axis direction are arranged at intervals in the Y-axis direction (see fig. 4).
The flat heat transfer tube 21 has a 1 st side 29a and a 2 nd side 29b with a width apart. Here, the 1 st side portion 29a is located on the leeward side, and the 2 nd side portion 29b is located on the windward side. The heat radiating fins 41 are attached to the main body 23.
The connection portion 25 has an open end surface 26, and an open end 28 (see fig. 5) of each of the plurality of flow paths 27 is located on the open end surface 26. Here, the opening end face 26 is arranged along the Y-axis direction. The connection portion 25 is connected to the header 31 so as to be inserted into an opening portion 33 formed in the header 31. The 1 st side portion 29a and the 2 nd side portion 29b of the connecting portion 25 are in contact with the opening inner wall surface 34 of the opening portion 33. As shown in fig. 4, in the main body 23, the plurality of flow passages 27 each have a 1 st flow passage cross-sectional area S1. As will be described later, in manufacturing the flat heat transfer tube 21, first, a molded body as the main body portion 23 is manufactured.
As shown in fig. 3 and 5, the connection portion 25 is subjected to a process (shrink tube) of shrinking the flat heat transfer tube 21 in the width direction (Y-axis direction). In the connecting portion 25, the 1 st side portion 29a is formed in a wedge shape so that the width thereof decreases as approaching the opening end face 26. On the opening end surface 26, the 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side 29a among the plurality of flow paths 27 arranged along the Y-axis direction narrows in the Y-axis direction so as to correspond to the 1 st side 29a formed in a wedge shape.
Therefore, the 1 st opening end 28a of the 1 st flow path 27a has a 2 nd flow path cross-sectional area S2 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27. That is, the 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side 29a has a 2 nd flow path cross-sectional area S2 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27. The outdoor heat exchanger 11 of embodiment 1 is configured as described above.
Next, an example of the method for manufacturing the outdoor heat exchanger 11 will be described with reference to the flowchart. As shown in fig. 6, first, in step T1, a material as a flat heat transfer tube is prepared. Next, in step T2, the material is put into an extrusion molding machine. Next, in step T3, the material fed into the extrusion molding machine is extruded, whereby a molded body 20 (see fig. 7) as a flat heat transfer tube is produced.
At this time, the plurality of channels 27 (see fig. 4) are each extrusion-molded so as to have the 1 st channel cross-sectional area S1, and thereby the cross-sectional shape of the molded body 20 (see fig. 7) is a cross-sectional shape that is symmetric about the center line in the width direction as shown in the cross-sectional shape of the main body 23 (see fig. 4). Thus, the material is uniformly extruded, and for example, a molded article having no voids can be produced.
Next, in step T4, the molded body 20 (see fig. 7) is cut and shrunk. As shown in fig. 7, the molded body 20 is cut in the Y-axis direction. The cut surface of the cut molded body 20 serves as an open end surface 26, and a plurality of flow paths 27 (see fig. 4 and the like) are opened in the open end surface 26.
At this time, the molded body 20 is cut and the shrinkage tube of the molded body 20 is performed. That is, the 1 st side 29a of the molded body 20 is pressed (see arrow P1) by a plate (not shown) or the like to reduce the width of the molded body 20 as approaching the opening end surface 26, for example, to form the 1 st side 29a in a wedge shape.
By forming the 1 st side portion 29a in a wedge shape, the 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side portion 29a among the plurality of flow paths 27 is narrowed in the Y-axis direction on the opening end surface 26 (refer to fig. 5). Thus, the 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side 29a has a 2 nd flow path cross-sectional area S2 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27. Thus, the flat heat transfer tube 21 including the main body portion 23 and the connection portion 25 is completed (step T5).
Next, in step T6, the flat heat transfer tube 21 is connected to the header 31 (see fig. 8). As shown in fig. 8, the connection portion 25 of the flat heat transfer tube 21 is inserted into the opening 33 provided in the header 31 as indicated by an arrow P3, and the 1 st side portion 29a and the 2 nd side portion 29b are brought into contact with the opening inner wall surface 34 of the opening 33.
At this time, since the 1 st side portion 29a is formed in a wedge shape, it is easily inserted into the opening 33 of the header 31. Further, the length of the connection portion 25 inserted into the header 31 is uniquely specified, so that the connection portion 25 can be prevented from being inserted into the opening portion 33 of the header 31, for example, more than necessary. In this way, the installation of the flat heat transfer tubes 21 to the header 31 is completed, and the main portion of the outdoor heat exchanger 11 is completed.
According to the outdoor heat exchanger 11 described above, first, when a molded body is produced as the flat heat transfer tube 21, a molded body having a cross-sectional shape symmetrical with respect to the center line in the width direction is molded as shown in the cross-sectional shape of the main body 23 (see fig. 4). This allows the material to be extruded uniformly, and for example, a molded article having no voids can be produced, thereby contributing to improvement in the manufacturability of the outdoor heat exchanger 11.
Next, by forming the 1 st side portion 29a in a wedge shape in the flat heat transfer tube 21 manufactured from the molded body, it is possible to improve manufacturability while ensuring heat transfer performance. This will be described.
As shown in fig. 2, in the outdoor heat exchanger 11 of the refrigeration cycle apparatus 1, heat exchange is performed between the air (see arrow Y1) sent to the outdoor heat exchanger 11 and the refrigerant flowing through the flat heat transfer tubes 21. When the outdoor heat exchanger 11 functions as an evaporator, heat exchange is performed between the air sent to the outdoor heat exchanger 11 and the refrigerant flowing through the flat heat transfer tubes 21, and the temperature of the air decreases from the windward direction to the leeward direction.
That is, as shown in fig. 9 (middle section), the heat load becomes smaller as the ventilation distance of the air flowing from the windward to the leeward becomes longer. In a region (range) where the heat load is high, heat exchange between air and the refrigerant is actively performed. Therefore, when functioning as an evaporator, if the refrigerant is completely vaporized by heat exchange with air, the heat transfer performance cannot be improved any more.
Therefore, as shown in fig. 9 (upper stage), the cut portion of the molded body 20, which is the connection portion 25 of the flat heat transfer tube 21, is processed (contracted) so that the flow rate of the refrigerant flowing on the windward side is greater than the flow rate of the refrigerant flowing on the leeward side with respect to the portion that is the main body portion of the flat heat transfer tube 21. That is, the 1 st side portion 29a is subjected to wedge-shaped processing (shrink tube) so that the width thereof decreases as approaching the opening end surface 26 (from the width W1 to the width W2).
Therefore, in the connection portion 25 of the flat heat transfer tube 21, the 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side portion 29a located on the leeward side narrows down in the Y-axis direction so as to correspond to the 1 st side portion 29a formed in a wedge shape. Thus, the 1 st opening end 28a has a 2 nd flow path cross-sectional area S2 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27.
By making the 2 nd channel cross-sectional area S2 of the 1 st opening end 28a of the 1 st channel 27a located on the leeward side smaller than the 1 st channel cross-sectional area S1 of the opening ends 28 of the other channels 27, as shown in fig. 9 (lower stage), it is difficult for the refrigerant to flow into the 1 st channel 27a, and accordingly, more refrigerant flows into the channels 27 located on the windward side or the like where the heat load is high, whereby complete vaporization of the refrigerant can be suppressed. As a result, heat transfer performance as the outdoor heat exchanger 11 can be ensured.
In the outdoor heat exchanger 11 described above, the 1 st side portion 29a of the connection portion 25 of the flat heat transfer tube 21 connected to the header 31 is formed in a wedge shape, so that it is easily inserted into the opening 33 formed in the header 31. This can contribute to improvement in the manufacturability of the outdoor heat exchanger 11.
Further, by bringing the wedge-shaped 1 st side portion 29a of the connection portion 25 into contact with the opening inner wall surface 34 of the opening portion 33, the length of the connection portion 25 (flat heat transfer tube 21) inserted into the header 31 can be specified uniquely. This prevents the connection portion 25 from being inserted into the opening 33 of the header 31, for example, more than necessary. As a result, the flow of the refrigerant in the header 31 can be stabilized.
Embodiment 2.
An example of an outdoor heat exchanger as a heat exchanger according to embodiment 2 will be described. As shown in fig. 10 and 11, the opening end surface 26 of the flat heat transfer tube 21 is disposed in a direction inclined with respect to the Y-axis direction as the 3 rd direction so as to approach the main body portion 23 from the 1 st side portion 29a toward the 2 nd side portion 29b.
In the connection portion 25 of the flat heat transfer tube 21, the 1 st side portion 29a is formed in a wedge shape so that the width thereof decreases as approaching the opening end face 26. The 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side 29a has a 2 nd flow path cross-sectional area S2 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27.
The other structures are the same as those of the outdoor heat exchanger 11 shown in fig. 3 to 5, and therefore the same reference numerals are given to the same components, and the description thereof will not be repeated unless necessary.
Next, an example of the method for manufacturing the outdoor heat exchanger 11 will be described. After the steps similar to the steps T1, T2 and T3 shown in fig. 6, the molded body is cut and the tube is contracted (step T4).
As shown in fig. 12, the molded body 20 is cut in a direction inclined with respect to the Y-axis direction. The cut surface of the cut molded body 20 serves as an open end surface 26, and a plurality of flow paths 27 (see fig. 11) are opened in the open end surface 26. At this time, the molded body 20 is cut and the shrinkage tube of the molded body 20 is performed. That is, the 1 st side 29a of the molded body 20 is pressed (see arrow P1) by a plate (not shown) or the like to reduce the width of the molded body 20 as approaching the opening end surface 26, for example, to form the 1 st side 29a in a wedge shape.
By forming the 1 st side portion 29a in a wedge shape, the 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side portion 29a of the plurality of flow paths 27 has a 2 nd flow path cross-sectional area S2 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27 on the opening end surface 26. Thus, the flat heat transfer tube 21 including the main body portion 23 and the connection portion 25 is completed (step T5). Then, the flat heat transfer tubes 21 are mounted to the header 31 by the same process as in step T6, and the main portion of the outdoor heat exchanger 11 is completed.
According to the above-described outdoor heat exchanger 11, in addition to the effects of the outdoor heat exchanger 11 described in embodiment 1, the following effects can be obtained.
In the connection portion 25 of the flat heat transfer tube 21 of the outdoor heat exchanger 11 described above, the opening end surface 26 is disposed in a direction inclined with respect to the Y-axis direction so as to approach the main body portion 23 from the 1 st side portion 29a located on the leeward side toward the 2 nd side portion 29b located on the windward side.
Therefore, the length of the 2 nd flow path 27b on the leeward side is longer than the length of the 1 st flow path 27a on the windward side. Thus, the flow path resistance (frictional resistance) of the 2 nd flow path 27b on the leeward side is larger than the flow path resistance (frictional resistance) of the 1 st flow path 27a on the windward side, and the refrigerant easily flows into the 2 nd flow path 27b on the windward side.
Accordingly, by forming the 1 st side portion 29a in a wedge shape, more refrigerant flows into the flow path 27 located on the upstream side where the heat load is high, in addition to the effect that the refrigerant is less likely to flow into the 1 st flow path 27a located on the downstream side. As a result, the heat transfer performance as the outdoor heat exchanger 11 can be improved.
Embodiment 3.
An example of an outdoor heat exchanger as a heat exchanger according to embodiment 3 will be described. As shown in fig. 13 and 14, the opening end face 26 of the flat heat transfer tube 21 is arranged along the Y-axis direction.
In the connection portion 25 of the flat heat transfer tube 21, the 1 st side portion 29a is formed in a wedge shape so that the width thereof decreases as approaching the opening end face 26. The 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side 29a has a 2 nd flow path cross-sectional area S2 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27.
In the connecting portion 25, the 2 nd side portion 29b is formed in a wedge shape so that the width thereof decreases as approaching the opening end face 26. The 2 nd open end 28b of the 2 nd flow path 27b closest to the 2 nd side 29b has a 3 rd flow path cross-sectional area S3 smaller than the 1 st flow path cross-sectional area S1 of the open ends 28 of the other flow paths 27 and larger than the 2 nd flow path cross-sectional area S2.
The other structures are the same as those of the outdoor heat exchanger 11 shown in fig. 3 to 5, and therefore the same reference numerals are given to the same components, and the description thereof will not be repeated unless necessary.
Next, an example of the method for manufacturing the outdoor heat exchanger 11 will be described. After the steps similar to the steps T1, T2 and T3 shown in fig. 6, the molded body is cut and the tube is contracted (step T4).
As shown in fig. 15, the molded body 20 is cut along the Y-axis direction. The cut surface of the cut molded body 20 serves as an open end surface 26, and a plurality of flow paths 27 (see fig. 14) are opened in the open end surface 26. At this time, the molded body 20 is cut, and the 1 st side portion 29a and the 2 nd side portion 29b of the molded body 20 are formed in a wedge shape so that the width of the molded body 20 is reduced as approaching the opening end face 26, with respect to both the 1 st side portion 29a and the 2 nd side portion 29b of the molded body 20.
The wedge-shaped 1 st side portion 29a is formed by applying pressure (pressure a: refer to arrow P1). Further, the wedge-shaped 2 nd side portion 29B is formed by applying a pressure (pressure B: refer to arrow P2) smaller than the pressure a.
By setting the magnitude relation of the wedge-shaped pressure to be the pressure a > pressure B, the 2 nd opening end 28B of the 2 nd flow path 27B closest to the 2 nd side portion 29B in the opening end surface 26 is shorter in length narrowed in the Y-axis direction than the 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side portion 29a.
Thus, as shown in fig. 14, the 2 nd opening end 28b of the 2 nd flow path 27b is formed to have a 3 rd flow path cross-sectional area S3 larger than the 2 nd flow path cross-sectional area S2 of the 1 st opening end 28a of the 1 st flow path 27 a. Thus, the flat heat transfer tube 21 including the main body portion 23 and the connection portion 25 is completed (step T5).
Next, in step T6, the flat heat transfer tube 21 is connected to the header 31 (see fig. 16). As shown in fig. 16, the connection portion 25 of the flat heat transfer tube 21 is inserted into the opening 33 provided in the header 31 as indicated by an arrow P3, and the 1 st side portion 29a and the 2 nd side portion 29b are brought into contact with the opening inner wall surface 34 of the opening 33.
At this time, since both the 1 st side portion 29a and the 2 nd side portion 29b are formed in a wedge shape, they are easily inserted into the opening 33 of the header 31. Further, the length of the connection portion 25 inserted into the header 31 is uniquely specified, so that the connection portion 25 can be prevented from being inserted into the opening portion 33 of the header 31, for example, more than necessary. In this way, the installation of the flat heat transfer tubes 21 to the header 31 is completed, and the main portion of the outdoor heat exchanger 11 is completed.
According to the above-described outdoor heat exchanger 11, in addition to the effects of the outdoor heat exchanger 11 described in embodiment 1, the following effects can be obtained.
In the connection portion 25 of the flat heat transfer tube 21 of the outdoor heat exchanger 11, both the 1 st side portion 29a and the 2 nd side portion 29b are formed in a wedge shape. Thus, when the connection portion 25 of the flat heat transfer tube 21 is connected to the header 31, it is easier to insert the connection portion into the opening 33 formed in the header 31 than in the case where only the 1 st side portion 29a is formed in a wedge shape. As a result, the manufacturability of the outdoor heat exchanger 11 can be improved.
Further, by bringing the wedge-shaped 1 st side portion 29a and the wedge-shaped 2 nd side portion 29b of the connection portion 25 into contact with the opening inner wall surface 34 of the opening portion 33, the length of the connection portion 25 (flat heat transfer tube 21) inserted into the header 31 can be more reliably defined. This prevents the connection portion 25 from being inserted into the opening 33 of the header 31 beyond necessity. As a result, the flow of the refrigerant in the header 31 can be stabilized.
Further, on the opening end surface 26 of the connecting portion 25, the 2 nd opening end 28b of the 2 nd flow path 27b closest to the 2 nd side portion 29b has a 3 rd flow path cross-sectional area S3 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27 and larger than the 2 nd flow path cross-sectional area S2.
As a result, the flow of the refrigerant through the 2 nd flow path 27b, which is located on the windward side and in which the refrigerant is required to flow more, can be minimized by forming the 2 nd side 29b on the windward side into a wedge shape, which makes it difficult for the refrigerant to flow through the 2 nd flow path 27b. As a result, the heat transfer performance as the outdoor heat exchanger 11 can be maintained.
Embodiment 4.
An example of an outdoor heat exchanger as a heat exchanger according to embodiment 4 will be described. As shown in fig. 17 and 18, the opening end surface 26 of the flat heat transfer tube 21 is disposed in a direction inclined with respect to the Y-axis direction as the 3 rd direction so as to approach the main body portion 23 from the 1 st side portion 29a toward the 2 nd side portion 29b.
In the connection portion 25 of the flat heat transfer tube 21, the 1 st side portion 29a is formed in a wedge shape so that the width thereof decreases as approaching the opening end face 26. The 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side 29a has a 2 nd flow path cross-sectional area S2 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27.
The 2 nd side portion 29b is formed in a wedge shape so that its width becomes smaller as approaching the opening end face 26. The 2 nd open end 28b of the 2 nd flow path 27b closest to the 2 nd side 29b has a 3 rd flow path cross-sectional area S3 smaller than the 1 st flow path cross-sectional area S1 of the open ends 28 of the other flow paths 27 and larger than the 2 nd flow path cross-sectional area S2.
The other structures are the same as those of the outdoor heat exchanger 11 shown in fig. 3 to 5, and therefore the same reference numerals are given to the same components, and the description thereof will not be repeated unless necessary.
Next, an example of the method for manufacturing the outdoor heat exchanger 11 will be described. After the steps similar to the steps T1, T2 and T3 shown in fig. 6, the molded body is cut and the tube is contracted (step T4).
As shown in fig. 19, the molded body 20 is cut in a direction inclined with respect to the Y-axis direction. The cut surface of the cut molded body 20 serves as an open end surface 26, and a plurality of flow paths 27 (see fig. 18) are opened in the open end surface 26. At this time, the molded body 20 is cut, and the 1 st side portion 29a and the 2 nd side portion 29b of the molded body 20 are formed in a wedge shape so that the width of the molded body 20 is reduced as approaching the opening end face 26, with respect to both the 1 st side portion 29a and the 2 nd side portion 29b of the molded body 20.
The wedge-shaped 1 st side portion 29a is formed by applying pressure (pressure a: refer to arrow P1). Further, the wedge-shaped 2 nd side portion 29B is formed by applying a pressure (pressure B: refer to arrow P2) smaller than the pressure a.
By setting the magnitude relation of the wedge-shaped pressure to be the pressure a > pressure B, the 2 nd opening end 28B of the 2 nd flow path 27B closest to the 2 nd side portion 29B in the opening end surface 26 is shorter in length narrowed in the Y-axis direction than the 1 st opening end 28a of the 1 st flow path 27a closest to the 1 st side portion 29a.
Thus, as shown in fig. 18, the 2 nd opening end 28b of the 2 nd flow path 27b is formed to have a 3 rd flow path cross-sectional area S3 larger than the 2 nd flow path cross-sectional area S2 of the 1 st opening end 28a of the 1 st flow path 27 a. Thus, the flat heat transfer tube 21 including the main body portion 23 and the connection portion 25 is completed (step T5).
Next, in step T6, the flat heat transfer tube 21 is connected to the header 31. At this time, since both the 1 st side portion 29a and the 2 nd side portion 29b are formed in a wedge shape, they are easily inserted into the opening 33 of the header 31. Further, the length of the connection portion 25 inserted into the header 31 is uniquely defined, so that the connection portion 25 can be prevented from being inserted into the opening 33 of the header 31, for example, beyond necessity. In this way, the installation of the flat heat transfer tubes 21 to the header 31 is completed, and the main portion of the outdoor heat exchanger 11 is completed.
According to the above-described outdoor heat exchanger 11, both the effect of the outdoor heat exchanger 11 described in embodiment 2 and the effect of the outdoor heat exchanger 11 described in embodiment 3 can be obtained.
First, in the connection portion 25 of the flat heat transfer tube 21 of the outdoor heat exchanger 11, the opening end surface 26 is disposed in a direction inclined with respect to the Y-axis direction so as to approach the main body portion 23 from the 1 st side portion 29a toward the 2 nd side portion 29b.
Thus, the length of the 1 st flow path 27a is longer than the length of the 2 nd flow path 27b, and the flow path resistance (frictional resistance) of the 1 st flow path 27a is larger than the flow path resistance (frictional resistance) of the 2 nd flow path 27b, so that the refrigerant easily flows into the 2 nd flow path 27b located on the windward side.
In the connecting portion 25, both the 1 st side portion 29a and the 2 nd side portion 29b are formed in a wedge shape. The 2 nd opening end 28b of the 2 nd flow path 27b closest to the 2 nd side portion 29b has a 3 rd flow path cross-sectional area S3 smaller than the 1 st flow path cross-sectional area S1 of the opening ends 28 of the other flow paths 27 and larger than the 2 nd flow path cross-sectional area S2 on the opening end surface 26 of the connecting portion 25.
As a result, the flow of the refrigerant through the 2 nd flow path 27b, which is located on the windward side and in which the refrigerant is required to flow more, can be minimized by forming the 2 nd side 29b on the windward side into a wedge shape, which makes it difficult for the refrigerant to flow through the 2 nd flow path 27b. As a result, the heat transfer performance as the outdoor heat exchanger 11 can be maintained.
Further, since both the 1 st side portion 29a and the 2 nd side portion 29b are formed in a wedge shape in the connecting portion 25, insertion into the opening 33 formed in the header 31 is easier. As a result, the manufacturability of the outdoor heat exchanger 11 can be improved.
Further, by bringing the wedge-shaped 1 st side portion 29a and the wedge-shaped 2 nd side portion 29b of the connection portion 25 into contact with the opening inner wall surface 34 of the opening portion 33, it is possible to prevent the connection portion 25 from being inserted into the opening portion 33 of the header 31, for example, more than necessary. As a result, the flow of the refrigerant in the header 31 can be stabilized.
In the above embodiments, the outdoor heat exchanger 11 of a single row is described as an example (see fig. 2). The outdoor heat exchanger 11 may be a plurality of rows of the outdoor heat exchangers 11, or may be a two-row type of the outdoor heat exchanger 11 in which the outdoor heat exchanger 11a and the outdoor heat exchanger 11b are arranged along the direction in which the air flows, as shown in fig. 20.
In the outdoor heat exchanger 11, the outdoor heat exchangers 11 according to embodiments 1 to 4 can be applied to the portions of the outdoor heat exchanger 11a connected to the header 31a and the portions of the outdoor heat exchanger 11b connected to the header 31b, which are indicated by the dashed-line frames DL.
Further, the outdoor heat exchanger may be an outdoor heat exchanger in which 3 or more rows of outdoor heat exchangers are arranged. Further, the present invention can be applied not only to the outdoor heat exchanger 11 but also to the indoor heat exchanger 5 as needed.
The outdoor heat exchanger described in each embodiment may be combined as necessary.
The embodiment disclosed herein is an example and is not limited thereto. The scope of the present disclosure is not the above-described scope but is shown by the claims, and is intended to include all modifications within the meaning and scope equivalent to the claims.
Industrial applicability
The present disclosure is effectively utilized for a heat exchanger provided with a flat heat transfer tube.
Description of the reference numerals
1: a refrigeration cycle device; 3: a compressor; 5: an indoor heat exchanger; 7: a fan; 9: an expansion valve; 10: a housing; 11: an outdoor heat exchanger; 13: a propeller fan; 15: a four-way valve; 17: refrigerant piping; 20: a molded body; 21: a flat heat transfer tube; 23: a main body portion; 25: a connection part; 26: an open end face; 27: a flow path; 27a: a 1 st flow path; 27b: a 2 nd flow path; 28: an open end; 28a: 1 st open end; 28b: a 2 nd open end; 29a: a 1 st side portion; 29b: a 2 nd side portion; 31: a header; 33: an opening portion; 34: an opening inner wall surface; 41: a heat radiation fin; s1: the 1 st flow path cross-sectional area; s2: the 2 nd flow path cross-sectional area; s3: 3 rd flow path cross-sectional area; y1, P2, P3: arrow (insert); DL: and (3) a frame.
Claims (8)
1. A heat exchanger, wherein the heat exchanger has:
a flat heat transfer tube having a 1 st side portion and a 2 nd side portion, which are spaced apart in a 1 st direction, and extending in a 2 nd direction intersecting the 1 st direction, wherein a plurality of flow paths are arranged at intervals in the 1 st direction, and each of the plurality of flow paths extends in the 2 nd direction;
a header formed with an opening portion, the flat heat transfer tube being connected to the opening portion; and
the heat dissipation fins are arranged on the inner side of the heat dissipation plate,
the flat heat transfer tube is provided with:
a main body portion attached to the heat radiating fin; and
a connection portion having an opening end face, being inserted into the opening portion of the header to be connected to the header, the plurality of flow paths being opened at the opening end face,
in the main body portion, the plurality of flow paths each have a 1 st flow path cross-sectional area,
in the connecting portion, the 1 st side portion is formed in a wedge shape in such a manner that the width is reduced as approaching the opening end face,
on the opening end face, a 1 st opening end of a 1 st flow path closest to the 1 st side portion formed in a wedge shape of the plurality of flow paths has a 2 nd flow path cross-sectional area smaller than the 1 st flow path cross-sectional area.
2. The heat exchanger of claim 1, wherein,
in the connecting portion, the 2 nd side portion is formed in a wedge shape in such a manner that the width is reduced as approaching the opening end face,
the 2 nd opening end of the 2 nd channel closest to the 2 nd side portion formed in a wedge shape among the plurality of channels arranged along the 1 st direction has a 3 rd channel cross-sectional area smaller than the 1 st channel cross-sectional area and larger than the 2 nd channel cross-sectional area on the opening end surface.
3. A heat exchanger according to claim 1 or 2, wherein,
the 1 st side portion of the wedge shape is in contact with an opening inner wall surface of the opening portion of the header.
4. The heat exchanger of claim 2, wherein,
the 2 nd side portion of the wedge shape is in contact with an opening inner wall surface of the opening portion of the header.
5. The heat exchanger according to any one of claims 1 to 4, wherein,
the opening end face is arranged along the 1 st direction.
6. The heat exchanger according to any one of claims 1 to 4, wherein,
the opening end surface is disposed along a 3 rd direction intersecting the 1 st direction so as to approach the main body portion from the 1 st side portion toward the 2 nd side portion.
7. The heat exchanger according to any one of claims 1 to 6, wherein,
the flat heat transfer tube is configured such that the 1 st side portion is on the leeward side and the 2 nd side portion is on the windward side.
8. A refrigeration cycle apparatus, wherein,
the refrigeration cycle apparatus includes the heat exchanger according to any one of claims 1 to 7.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2021/004112 WO2022168232A1 (en) | 2021-02-04 | 2021-02-04 | Heat exchanger and refrigeration cycle apparatus equipped with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116802453A true CN116802453A (en) | 2023-09-22 |
Family
ID=82740992
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202180091905.2A Pending CN116802453A (en) | 2021-02-04 | 2021-02-04 | Heat exchanger and refrigeration cycle device provided with same |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20240003636A1 (en) |
| EP (1) | EP4290170A4 (en) |
| JP (1) | JP7483062B2 (en) |
| CN (1) | CN116802453A (en) |
| WO (1) | WO2022168232A1 (en) |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5069277A (en) * | 1990-03-13 | 1991-12-03 | Diesel Kiki Co., Ltd. | Vehicle-loaded heat exchanger of parallel flow type |
| JPH06341789A (en) * | 1993-06-01 | 1994-12-13 | Mitsubishi Heavy Ind Ltd | Heat exchanger |
| JP2672463B2 (en) * | 1994-03-15 | 1997-11-05 | 昭和アルミニウム株式会社 | Method for producing flat tube for heat exchanger |
| JP2001174188A (en) * | 1999-12-16 | 2001-06-29 | Zexel Valeo Climate Control Corp | Serpentine type heat exchanger and method of manufacturing tube used therefor |
| JP2002130983A (en) | 2000-10-26 | 2002-05-09 | Toyo Radiator Co Ltd | Extruded tube having multiple minute holes for heat exchanger, and heat exchanger |
| JP4962278B2 (en) * | 2007-11-15 | 2012-06-27 | 三菱電機株式会社 | Heat exchanger and heat pump system |
| US8234881B2 (en) | 2008-08-28 | 2012-08-07 | Johnson Controls Technology Company | Multichannel heat exchanger with dissimilar flow |
| JP6200280B2 (en) | 2013-11-05 | 2017-09-20 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Method for expanding heat exchanger tube and air conditioner |
| JP2017026281A (en) * | 2015-07-28 | 2017-02-02 | サンデンホールディングス株式会社 | Heat exchanger |
| JP2017190896A (en) | 2016-04-12 | 2017-10-19 | 株式会社デンソー | Heat exchanger |
-
2021
- 2021-02-04 JP JP2022579238A patent/JP7483062B2/en active Active
- 2021-02-04 US US18/254,794 patent/US20240003636A1/en active Pending
- 2021-02-04 EP EP21924628.7A patent/EP4290170A4/en active Pending
- 2021-02-04 WO PCT/JP2021/004112 patent/WO2022168232A1/en active Application Filing
- 2021-02-04 CN CN202180091905.2A patent/CN116802453A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2022168232A1 (en) | 2022-08-11 |
| WO2022168232A1 (en) | 2022-08-11 |
| EP4290170A1 (en) | 2023-12-13 |
| JP7483062B2 (en) | 2024-05-14 |
| US20240003636A1 (en) | 2024-01-04 |
| EP4290170A4 (en) | 2024-03-06 |
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