CN112567192A - Heat exchanger, heat exchanger unit, and refrigeration cycle device - Google Patents
Heat exchanger, heat exchanger unit, and refrigeration cycle device Download PDFInfo
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- CN112567192A CN112567192A CN201880095774.3A CN201880095774A CN112567192A CN 112567192 A CN112567192 A CN 112567192A CN 201880095774 A CN201880095774 A CN 201880095774A CN 112567192 A CN112567192 A CN 112567192A
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- flat tube
- heat exchanger
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- tube
- tubes
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- 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
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
- F28D1/0435—Combination of units extending one behind the other
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- 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
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
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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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
- F28F1/20—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being attachable to the element
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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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
- F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
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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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
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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
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
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- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
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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
- F28F2215/00—Fins
- F28F2215/02—Arrangements of fins common to different heat exchange sections, the fins being in contact with different heat exchange media
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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
- F28F2215/00—Fins
- F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
Abstract
A heat exchanger, a heat exchanger unit, and a refrigeration cycle device are provided in which the pressure resistance of a tube through which a refrigerant flows is improved, the weight of heat transfer fins is reduced, and the manufacture is easy. The present invention is provided with: a 1 st flat tube group including a plurality of flat tubes arranged with their tube axes parallel; a 2 nd flat tube group which is disposed adjacent to the 1 st flat tube group and includes a plurality of flat tubes arranged with their tube axes parallel to each other; a 1 st flat tube, which is 1 of a plurality of flat tubes included in a 1 st flat tube group, and a 2 nd flat tube, which is 1 of the plurality of flat tubes included in a 2 nd flat tube group; and fins provided on the 1 st flat tube and the 2 nd flat tube. The fin includes a 1 st portion connecting an end of a long axis in a cross section perpendicular to the tube axis of the 1 st flat tube and an end of a long axis in a cross section perpendicular to the tube axis of the 2 nd flat tube.
Description
Technical Field
The present invention relates to a heat exchanger, a heat exchanger unit including the heat exchanger, and a refrigeration cycle apparatus, and particularly relates to a structure of fins attached to flat tubes.
Background
Among conventional heat exchangers, the following multi-tube heat exchangers are known: in order to improve the heat exchange performance, 2 plates were attached, and the tube bodies having a small diameter were arranged in a staggered configuration and connected to each other by heat transfer fins. (see, for example, patent document 1).
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 2006 and 084078
Disclosure of Invention
Problems to be solved by the invention
However, in the conventional heat exchanger disclosed in patent document 1, since the tube body is configured by bonding 2 plates, there is a problem that the heat transfer fins are also thickened and increased in weight in order to ensure pressure resistance of the tube body. Further, there is a problem that the brazing material to which 2 sheets are bonded and joined enters the refrigerant flow path inside the tube body portion.
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat exchanger, a heat exchanger unit, and a refrigeration cycle apparatus, in which pressure resistance of a tube through which a refrigerant flows is improved, weight of a heat transfer fin is also reduced, and manufacturing is also easy.
Means for solving the problems
The heat exchanger of the present invention comprises: a 1 st flat tube group including a plurality of flat tubes arranged with their tube axes parallel; a 2 nd flat tube group that is disposed adjacent to the 1 st flat tube group and includes the plurality of flat tubes arranged with the tube axes parallel to each other; a 1 st flat tube that is 1 of the plurality of flat tubes included in the 1 st flat tube group and a 2 nd flat tube that is 1 of the plurality of flat tubes included in the 2 nd flat tube group; and fins provided on the 1 st flat tube and the 2 nd flat tube, the fins including 1 st portions, the 1 st portions connecting ends of the 1 st flat tube with ends of the 2 nd flat tube with respect to a long axis in a cross section perpendicular to the tube axis.
The heat exchanger unit of the present invention includes the heat exchanger described above.
The refrigeration cycle apparatus of the present invention includes the heat exchanger unit.
Effects of the invention
According to the present invention, since the plurality of flat tube groups each including the plurality of flat tubes are connected by the fins, the pressure resistance of the tubes through which the refrigerant flows can be improved, and the fins can be formed thin, so that the weight of the fins can be reduced. Further, a heat exchanger unit, and a refrigeration cycle device having high heat exchange performance and easy to manufacture can be obtained.
Drawings
Fig. 1 is a front view showing a heat exchanger according to embodiment 1.
Fig. 2 is a side view showing a heat exchanger according to embodiment 1.
Fig. 3 is an explanatory diagram of a refrigeration cycle apparatus to which the heat exchanger of embodiment 1 is applied.
Fig. 4 is an explanatory view of a sectional structure of the heat exchanger of fig. 2.
Fig. 5 is a side view of a heat exchanger according to a modification of the heat exchanger of embodiment 1.
Fig. 6 is an explanatory diagram of a cross-sectional structure of a heat exchanger according to a modification of the heat exchanger of embodiment 1.
Fig. 7 is an enlarged view of the slit as viewed from the x direction.
Fig. 8 is an explanatory diagram of a cross-sectional structure of a heat exchanger according to a modification of the heat exchanger of embodiment 1.
Detailed Description
Hereinafter, embodiments of the heat exchanger and the heat exchanger unit will be described. The form of the drawings is an example, and the present invention is not limited thereto. In the drawings, the same or corresponding portions are denoted by the same reference numerals and are common throughout the specification. In the following drawings, the relationship between the sizes of the respective constituent members may be different from the actual one.
Embodiment mode 1
Fig. 1 is a front view showing a heat exchanger 100 according to embodiment 1. Fig. 2 is a side view showing the heat exchanger 100 according to embodiment 1. Fig. 3 is an explanatory diagram of the refrigeration cycle apparatus 1 to which the heat exchanger 100 of embodiment 1 is applied. The heat exchanger 100 shown in fig. 1 and 2 is mounted on a refrigeration cycle apparatus 1 such as an air conditioner or a refrigerator. As shown in fig. 3, the refrigeration cycle apparatus 1 is connected to a compressor 3, a four-way valve 4, an outdoor heat exchanger 5, an expansion device 6, and an indoor heat exchanger 7 by refrigerant pipes 90 to form a refrigerant circuit. For example, when the refrigeration cycle apparatus 1 is an air conditioner, the refrigerant can be switched to a heating operation, a cooling operation, or a defrosting operation by flowing through the refrigerant pipe 90 and switching the flow of the refrigerant by the four-way valve 4.
The outdoor heat exchanger 5 mounted on the outdoor unit 8 and the indoor heat exchanger 7 mounted on the indoor unit 9 include the blower 2 in the vicinity thereof. In the outdoor unit 8, the blower 2 sends outside air to the outdoor heat exchanger 5, and heat exchange is performed between the outside air and the refrigerant. In the indoor unit 9, the blower 2 sends indoor air to the indoor heat exchanger 7, and heat exchange is performed between the indoor air and the refrigerant to adjust the temperature of the indoor air. The heat exchanger 100 can be used as the outdoor heat exchanger 5 mounted on the outdoor unit 8 and the indoor heat exchanger 7 mounted on the indoor unit 9 in the refrigeration cycle apparatus 1, and can function as a condenser or an evaporator. The outdoor unit 8 and the indoor unit 9 on which the heat exchanger 100 is mounted are particularly referred to as a heat exchanger unit.
The heat exchanger 100 shown in fig. 1 includes 2 flat tube groups 10. One of the 2 flat tube groups 10 is referred to as a 1 st flat tube group 10a, and the other is referred to as a 2 nd flat tube group 10 b. The flat tube groups 10a and 10b may be collectively referred to as a flat tube group 10. The 1 st and 2 nd flat tube groups 10a and 10b are aligned in the x direction. The flat tube group 10 includes a plurality of flat tubes 20. The plurality of flat tubes 20 are shown as 20a and 20b in fig. 1 and 2. The plurality of flat tubes 20 of each flat tube group 10 are arranged with their tube axes parallel to each other in the y direction. In embodiment 1, the tube axes of the plurality of flat tubes 20 face the z direction. In embodiment 1, the direction opposite to the z direction coincides with the direction of gravity, but the heat exchanger 100 may be arranged such that the z axis is inclined with respect to the direction of gravity. The plurality of flat tubes 20a of the 1 st flat tube group 10a are connected to the lower header 50a at the lower end in the tube axis direction and to the upper header 51a at the upper end in the tube axis direction. Similarly, the plurality of flat tubes 20b of the 2 nd flat tube group 10b are connected to the lower header 50b at the lower end in the tube axis direction and connected to the upper header 51b at the upper end in the tube axis direction. In embodiment 1, the heat exchanger 100 includes 2 flat tube groups 10a and 10b, but may include more flat tube groups 10.
Fig. 4 is an explanatory diagram of a sectional configuration of the heat exchanger 100 of fig. 2. Fig. 4 is a cross section perpendicular to tube axes of the plurality of flat tubes 20 included in each of the plurality of flat tube groups 10, and is an explanatory view of a structure of a cross section corresponding to the section a-a in fig. 2. Fig. 4 shows a part of the plurality of flat tubes 20 constituting each flat tube group 10. The plurality of flat tubes 20a of the 1 st flat tube group 10a and the plurality of flat tubes 20b of the 2 nd flat tube group 10b have their major axes arranged in the x direction and their minor axes arranged in the y direction in a cross section perpendicular to the tube axes. The plurality of flat tubes 20a of the 1 st flat tube group 10a and the plurality of flat tubes 20b of the 2 nd flat tube group 10b are arranged alternately. That is, the 2 nd flat tube 20b of the 2 nd flat tube group 10b is disposed at a position shifted in the y direction from the extension line of the major axis of the 1 st flat tube 20a of the 1 st flat tube group 10a, and the 2 nd flat tube 20b is disposed on the extension line of the gap between the adjacent 21 st flat tubes 20a when viewed in the x direction. Hereinafter, the 1 st flat tube 20a and the 2 nd flat tube 20b may be collectively referred to as the flat tubes 20.
As shown in fig. 4, fins 30 are provided on the 1 st flat tube 20a of the 1 st flat tube group 10a and the 2 nd flat tube 20b of the 2 nd flat tube group 10 b. The fins 30 are formed by bending 1 plate-like member, and the plate surfaces are provided along the 1 st flat tube 20a and the 2 nd flat tube 20 b. In embodiment 1, since the tube axes of the 1 st flat tube 20a and the 2 nd flat tube 20b coincide with the direction of gravity, the fins 30 are arranged so that the plate surfaces thereof are along the direction of gravity. Therefore, the heat exchanger 100 can discharge condensed water adhering to the fins 30 due to dew condensation when functioning as an evaporator, and melted water of frost generated by a defrosting (defrost) operation when frost formation occurs, from the fins 30 without stagnation. Thereby, the heat exchange performance of the heat exchanger 100 is maintained high.
The fin 30 includes a 1 st portion 31 disposed between the 1 st flat tube 20a and the 2 nd flat tube 20b, a 2 nd portion 32 joined to the 1 st flat tube 20a, a 3 rd portion 33 joined to the 2 nd flat tube 20b, a 4 th portion 34 extending in the direction opposite to the x direction from the end portion 21a of the 1 st flat tube 20a, and a 5 th portion 35 extending in the x direction from the end portion 22b of the 2 nd flat tube 20 b.
The fin 30 and the 1 st flat tube 20a are joined to each other at the 2 nd portion 32 by brazing or the like. The 2 nd portion 32 is formed with a concave shape along the side surface shape of the 1 st flat tube 20a by bending a plate-like member, and the 1 st flat tube 20a is fitted into the concave shape. The fins 30 and the 2 nd flat tubes 20b are joined to each other at the 3 rd portions 33 by brazing or the like. The 3 rd portion 33 is also formed with a concave shape along the side surface shape of the 2 nd flat tube 20b by bending a plate-like member, and the 2 nd flat tube 20b is fitted into the concave shape. The concave shapes of the 2 nd and 3 rd portions 32, 33 of the fin 30 face different directions. The concave shape of the 2 nd part 32 is a concave shape that opens in the y direction, and the concave shape of the 3 rd part 33 is a concave shape that opens in the opposite direction to the y direction. That is, the 1 st flat tube 20a is attached to one plate surface 38 of the fin 30 facing the y direction, and the 2 nd flat tube 20b is attached to the other plate surface 39 of the fin 30 facing the opposite direction to the y direction.
As shown in fig. 4, the 1 st flat tube 20a and the 2 nd flat tube 20b are fitted into the concave shape of the 1 fin 30. In this way, the fins 30, the 1 st flat tube 20a, and the 2 nd flat tube 20b can be handled as an integral component during manufacture. That is, since 2 flat tubes 20 can be fitted into the concave shape of 1 fin 30 and integrated therewith before being joined to the lower end headers 50a, 50b and the upper end headers 51a, 51b, positioning of the 2 flat tubes 20 before being joined becomes easy, and assembling workability can be improved.
The fin 30 includes a 1 st portion 31 located between the 1 st and 2 nd flat tube groups 10a and 10 b. The 1 st portion 31 is arranged to connect the end of the concave shape into which the 1 st flat tube 20a fits and the end of the concave shape into which the 2 nd flat tube 20b fits. In other words, the 1 st portion 31 is arranged to connect the end portions 22a, 21b, the end portions 22a being the end portions of the 1 st flat tubes 20a on the 2 nd flat tube group 10b side, and the end portions 21b being the end portions of the 2 nd flat tubes 20b on the 1 st flat tube group 10a side. In embodiment 1, the 1 st portion 31 is disposed obliquely to the long axis of the 1 st flat tube 20a and the 2 nd flat tube 20 b.
As shown in fig. 4, in embodiment 1, air flows in the x direction with respect to the heat exchanger 100. As described above, the 1 st portion 31 of the fin 30 is arranged obliquely, so that the air flows zigzag in the gap between the 1 st flat tube 20a, the 2 nd flat tube 20b, and the fin 30. Therefore, the heat transfer area of the heat exchanger 100 is enlarged, and the heat transfer performance is improved. In addition, at the 1 st portions 31 of the fins 30, the wind is turned, and the flowing air collides with the side walls 23b of the 2 nd flat tubes 20 b. Since the flow of air between the 2 nd flat tubes 20b is disturbed by the collision of air, the temperature of air in contact with each portion of the 2 nd flat tubes 20b is easily equalized, and the dryness of the refrigerant flowing in the 2 nd flat tubes 20b is equalized. This improves the heat exchange performance of the heat exchanger 100.
The fin 30 includes a 4 th portion 34 having a flat plate shape, and the 4 th portion 34 extends from an end portion 21a facing the direction opposite to the x direction among the end portions of the 1 st flat tube 20 a. That is, the 4 th portion 34 is provided extending from the end 21a on the opposite side of the end 22a where the 1 st portion 31 is provided extending, among the ends of the 1 st flat tube 20 a. The fin 30 includes a 5 th portion 35 having a flat plate shape, and the 5 th portion 35 extends from the end 22b facing the x direction among the end portions of the 2 nd flat tube 20 b. That is, the 5 th portion 35 is extended from the end portion 22b on the opposite side from the end portion 21b where the 1 st portion 31 is extended, among the end portions of the 2 nd flat tube 20 b. Since the fin 30 includes the 4 th portion 34 and the 5 th portion 35, the heat transfer area of the heat exchanger 100 is enlarged and the heat transfer performance is improved.
Fig. 5 is a side view of a heat exchanger 100a according to a modification of the heat exchanger 100 according to embodiment 1. Fig. 6 is an explanatory diagram of a cross-sectional structure of a heat exchanger 100a according to a modification of the heat exchanger 100 of embodiment 1. Fig. 7 is an enlarged view of the slit 41 as viewed from the x direction. Fig. 6 is an explanatory diagram of a sectional configuration corresponding to the section B-B of fig. 5. The heat exchanger 100a is provided with the slits 41 in the 4 th portions 34 located on the windmost side of the fins 30 and extending from the end portions 21a of the 1 st flat tubes 20 a. The slit 41 is formed by cutting out a part of the 4 th part 34 in a direction perpendicular to the plate surface. As shown in fig. 7, the plate-shaped 4 th part 34 is formed with a parallel portion 45 and an upright portion 44, the parallel portion 45 being a portion where a part of the 4 th part 34 is cut and raised and being positioned substantially parallel to the 4 th part 34, and the upright portion 44 being a portion where the plate surface of the 4 th part 34 is connected from both ends of the parallel portion 45. By providing the parallel portion 45 in parallel with the plate surface of the 4 th portion 34 of the fin 30, the boundary layer of the flow of air flowing in parallel with the surface of the 4 th portion 34 can be reduced, the heat transfer performance can be improved, and an increase in the ventilation resistance can be suppressed.
The heat exchanger 100a also has slits 41 in the 5 th portions 35 located on the downwind side of the fins 30 and extending from the end portions 21b of the 2 nd flat tubes 20 b. At the 5 th portion 35, the slit 41 is also provided in the same configuration as the 4 th portion 34. Therefore, the boundary layer of the flow of the air flowing in parallel with the surface of the 5 th portion 35 becomes small, and it is possible to improve the heat transfer performance and suppress an increase in the ventilation resistance.
The heat exchanger 100a includes louvers (lovers) 40 in a 1 st portion 31 located between the 1 st flat tube 20a and the 2 nd flat tube 20 b. The louver 40 is a tongue-shaped piece formed by cutting and dividing a part of the plate-shaped 1 st portion 31 and extending in the x direction in parallel with the long axes of the 1 st flat tube 20a and the 2 nd flat tube 20 b. Further, an opening penetrating the plate surface of the 1 st part 31 is formed in the root of the louver 40. The louver 40 extends in parallel with the flow of air passing between the 1 st flat tubes 20 a. Therefore, the air passes through the holes formed in the panel surface of the portion of the 1 st section 31 where the louver 40 is disposed. This makes it possible to form a flow of air parallel to the long axis of the flat tube 20 even in a portion where the 1 st portion 31 inclined with respect to the 1 st flat tube 20a is provided. Therefore, the heat transfer performance can be improved and the increase of the ventilation resistance of the heat exchanger 100a can be suppressed by the louver 40.
The heat exchangers 100 and 100a are manufactured by the following steps. First, the plurality of fins 30 are combined with the 1 st and 2 nd flat tube groups 10a and 10 b. Each flat tube 20 is fitted into the concave shape of the fin 30. In a state where the 1 st flat tube 20a, the 2 nd flat tube 20b, and the fins 30 are integrated, the ends of the 1 st flat tube 20a and the 2 nd flat tube 20b in the tube axis direction are inserted into the lower end headers 50a, 50b or the upper end headers 51a, 51 b. After that, the fin 30 is pulled from the 4 th and 5 th parts 34 and 35 located at both ends in the x direction of fig. 4 and 6. Thereby, the 2 nd portion 32 of the fin 30 is pressed against the 1 st flat tube 20a, and the 3 rd portion 33 is pressed against the 2 nd flat tube 20 b. This brings the fins 30 into contact with the plurality of flat tubes 20, thereby improving the accuracy of mounting the fins 30 to the flat tubes 20. In this state, the plurality of flat tubes 20a and 20b are directly inserted into the lower end headers 50a and 50b and the upper end headers 51a and 51 b. Then, brazing filler metal is placed at the joint portions between the plurality of flat tubes 20a, 20b and the lower end headers 50a, 50b and the upper end headers 51a, 51b, and the joint portions between the plurality of flat tubes 20a, 20b and the fins 30, and the brazing filler metal is placed in a furnace and brazed. The heat exchangers 100 and 100a can integrally treat the 1 st and 2 nd flat tube groups 10a and 10b with the plurality of fins 30, and therefore have the advantage of being easy to assemble and easy to manufacture.
In embodiment 1, the 1 st flat tube 20a and the 2 nd flat tube 20b are arranged in a staggered manner so that the major axes thereof are parallel to each other, and therefore, the 1 st portion 31 is arranged obliquely to the 1 st flat tube 20a and the 2 nd flat tube 20b, but the invention is not limited to this. Further, as a modification of the heat exchanger 100 according to embodiment 1, the heat exchanger 100a in which both the louver 40 and the slit 41 are formed has been described, but the heat exchanger may be one in which either the louver 40 or the slit 41 is formed.
Fig. 8 is an explanatory diagram of a cross-sectional structure of a heat exchanger 100b of a modification of the heat exchanger 100 of embodiment 1. Fig. 8 is an explanatory view of a cross section corresponding to the section a-a in fig. 2. In the heat exchanger 100b of the modification, the 1 st portion 31 of the fin 30, the 2 nd portion 32 into which the 1 st flat tube 20a is fitted, and the 3 rd portion 33 into which the 2 nd flat tube 20b is fitted are parallel. The 4 th portion 34 on the windmost side and the 5 th portion 35 on the downmost side of the fin 30 are inclined with respect to the 1 st portion 31, the 2 nd portion 32 in which the 1 st flat tube 20a is embedded, and the 3 rd portion 33 in which the 2 nd flat tube 20b is embedded. Therefore, the air flowing in the x direction with respect to the heat exchanger 100 collides with the side walls 23a of the 1 st flat tube 20 a. Since the flow of air between the 1 st flat tubes 20a is disturbed by the collision of air, the temperature of air in contact with each portion of the 1 st flat tube 20a is easily equalized, and the dryness of the refrigerant flowing in the 1 st flat tube 20a is equalized. This improves the heat exchange performance of the heat exchanger 100 b.
The heat exchangers 100, 100a, and 100b according to embodiment 1 are used in at least one of the outdoor heat exchanger 5 and the indoor heat exchanger 7 of the refrigeration cycle apparatus 1 shown in fig. 3, and thus the refrigeration cycle apparatus 1 having high energy efficiency can be provided. Here, the energy efficiency is defined by "heating energy efficiency ═ indoor heat exchanger (condenser) capacity/total input", and "cooling energy efficiency ═ indoor heat exchanger (evaporator) capacity/total input".
In addition, the heat exchangers 100, 100a, and 100b, the heat exchanger unit, and the refrigeration cycle apparatus 1 using the heat exchanger unit described in embodiment 1 above can achieve the effects in the case of the refrigerant such as R410A, R32, HFO1234yf, and the like. Further, in embodiment 1, an example of air and a refrigerant is shown as the working fluid, but the same effect is obtained by using other gas, liquid, or gas-liquid mixed fluid.
The respective structures of the heat exchangers 100, 100a, and 100b according to embodiment 1 can be combined as appropriate. For example, both or either one of louver 40 and slit 41 of heat exchanger 100a may be applied to heat exchanger 100 b.
Description of the reference numerals
1 refrigeration cycle device, 2 blower, 3 compressor, 4 four-way valve, 5 outdoor heat exchanger, 6 expansion device, 7 indoor heat exchanger, 8 outdoor unit, 9 indoor unit, 10 flat tube group, 10a (1 st) flat tube group, 10b (2 nd) flat tube group, 20 flat tube, 20a (1 st) flat tube, 20b (2 nd) flat tube, 21a end, 21b end, 22a end, 22b end, 23a side wall, 23b side wall, 30 fin, 31 st portion, 32 nd portion, 33 rd portion, 3 rd portion, 34 th portion, 5 th portion, 38 plate surface, 39 plate surface, 40 louver, 41 slit, 44 rising portion, 45 parallel portion, 50 lower end header, 50a lower end header, 50b lower end header, 51 upper end header, 51a upper end header, 51b upper end header, 90 refrigerant piping, 100 heat exchanger, 100a heat exchanger, 6 heat exchanger, 1b heat exchanger, and heat exchanger, 100b heat exchanger.
Claims (9)
1. A heat exchanger is provided with:
a 1 st flat tube group including a plurality of flat tubes arranged with their tube axes parallel;
a 2 nd flat tube group that is disposed adjacent to the 1 st flat tube group and includes the plurality of flat tubes arranged with the tube axes parallel to each other;
a 1 st flat tube that is 1 of the plurality of flat tubes included in the 1 st flat tube group and a 2 nd flat tube that is 1 of the plurality of flat tubes included in the 2 nd flat tube group; and
fins provided on the 1 st flat tube and the 2 nd flat tube,
the fin includes a 1 st portion connecting an end of a long axis in a cross section perpendicular to the tube axis of the 1 st flat tube and an end of the long axis in a cross section perpendicular to the tube axis of the 2 nd flat tube.
2. The heat exchanger of claim 1,
the plurality of flat tubes of the 1 st flat tube group and the plurality of flat tubes of the 2 nd flat tube group are arranged in a staggered pattern.
3. The heat exchanger according to claim 1 or 2,
the fin is provided with:
a 2 nd portion joined to the side wall of the 1 st flat tube; and
a 3 rd portion joined to the side wall of the 2 nd flat tube,
the 2 nd portion is joined to the 1 st flat tube on one surface side of the plate surface of the fin,
the 3 rd portion is joined to the 2 nd flat tube on the other side of the plate surface.
4. A heat exchanger according to any one of claims 1 to 3,
the 1 st portions of the fins located between adjacent groups of the plurality of flat tubes are inclined with respect to the long axes of the plurality of flat tubes.
5. The heat exchanger of claim 4,
the 1 st part is provided with:
a louver extending from the plate surface in a direction intersecting the pipe axis;
and an opening formed at a root portion of the louver on the plate surface side and penetrating the plate surface.
6. The heat exchanger of claim 5,
the louvers are parallel to the long axis of the plurality of flat tubes.
7. The heat exchanger according to any one of claims 1 to 6,
the fin is provided with:
a 4 th portion extending from an end portion of the 1 st flat tube on the opposite side of the end portion of the long axis from which the 1 st portion extends; and
a 5 th portion extending from an end portion of the 2 nd flat tube on the opposite side of the end portion from which the 1 st portion extends,
at least one of the 4 th part and the 5 th part has a slit formed in the plate surface.
8. A heat exchanger unit comprising the heat exchanger according to any one of claims 1 to 7.
9. A refrigeration cycle apparatus comprising the heat exchanger unit according to claim 8.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2018/031502 WO2020044391A1 (en) | 2018-08-27 | 2018-08-27 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112567192A true CN112567192A (en) | 2021-03-26 |
Family
ID=69643578
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880095774.3A Pending CN112567192A (en) | 2018-08-27 | 2018-08-27 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3845851B1 (en) |
| JP (1) | JP6980117B2 (en) |
| CN (1) | CN112567192A (en) |
| WO (1) | WO2020044391A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022085067A1 (en) * | 2020-10-20 | 2022-04-28 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
| CN112277570B (en) * | 2020-10-30 | 2022-05-20 | 安徽江淮汽车集团股份有限公司 | Warm braw core and vehicle air conditioner |
| JPWO2023105566A1 (en) * | 2021-12-06 | 2023-06-15 |
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| JP6719657B2 (en) * | 2017-04-04 | 2020-07-08 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
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| WO2019026239A1 (en) * | 2017-08-03 | 2019-02-07 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
| CN208238599U (en) * | 2018-05-18 | 2018-12-14 | 广东美的制冷设备有限公司 | Heat exchanger and heat exchange equipment |
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2018
- 2018-08-27 EP EP18932105.2A patent/EP3845851B1/en active Active
- 2018-08-27 JP JP2020539169A patent/JP6980117B2/en active Active
- 2018-08-27 WO PCT/JP2018/031502 patent/WO2020044391A1/en unknown
- 2018-08-27 CN CN201880095774.3A patent/CN112567192A/en active Pending
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| DE1927605A1 (en) * | 1969-05-30 | 1970-12-03 | Hans Henting | Weather cooler for mining, especially face cooler |
| DE2154366A1 (en) * | 1971-11-02 | 1973-05-10 | Folle Willi | AIR INLET BLINDS |
| JPH07305986A (en) * | 1994-05-16 | 1995-11-21 | Sanden Corp | Multitubular type heat exchanger |
| JP2000088297A (en) * | 1998-09-17 | 2000-03-31 | Hitachi Ltd | Ice heat storage type air-conditioning device and ice heat storage tank |
| WO2002016834A2 (en) * | 2000-08-21 | 2002-02-28 | Engineered Dynamics Corporation | Heat exchanger assembly and a method for efficiently transferring heat |
| CN1523317A (en) * | 2003-02-20 | 2004-08-25 | 松下电器产业株式会社 | Outdoor heat exchanger for heat pump |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP3845851A1 (en) | 2021-07-07 |
| WO2020044391A1 (en) | 2020-03-05 |
| JP6980117B2 (en) | 2021-12-15 |
| EP3845851A4 (en) | 2021-09-01 |
| EP3845851B1 (en) | 2023-03-01 |
| JPWO2020044391A1 (en) | 2021-05-13 |
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Application publication date: 20210326 |
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