CN118339417A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN118339417A CN118339417A CN202180104564.8A CN202180104564A CN118339417A CN 118339417 A CN118339417 A CN 118339417A CN 202180104564 A CN202180104564 A CN 202180104564A CN 118339417 A CN118339417 A CN 118339417A
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- Prior art keywords
- heat transfer
- transfer promoting
- heat
- portions
- promoting
- Prior art date
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- 230000001737 promoting effect Effects 0.000 claims abstract description 241
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 18
- 239000003507 refrigerant Substances 0.000 description 27
- 238000010586 diagram Methods 0.000 description 20
- 230000004048 modification Effects 0.000 description 7
- 238000012986 modification Methods 0.000 description 7
- 238000001816 cooling Methods 0.000 description 6
- 238000010438 heat treatment Methods 0.000 description 6
- 238000009826 distribution Methods 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 4
- 230000000052 comparative effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 238000004080 punching Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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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
-
- 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
- F28F1/16—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 integral with the element, e.g. formed by extrusion
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
-
- 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
-
- 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
- F28F2215/00—Fins
- F28F2215/08—Fins with openings, e.g. louvers
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
The heat exchanger comprises: a heat transfer pipe extending in a2 nd direction intersecting the 1 st direction of the gas flow; and a fin provided to the heat transfer pipe and having a surface along the 1 st and 2 nd directions, the fin having: a 1 st extension portion provided on the upstream side of the heat transfer tube with respect to the gas in the 1 st direction, the extension portion having a 1 st heat transfer promoting region for improving the heat transfer rate; and a2 nd extension portion provided on the downstream side of the heat transfer pipe with respect to the gas in the 1 st direction, and having a2 nd heat transfer promoting region for improving the heat transfer rate.
Description
Technical Field
The present disclosure relates to heat exchangers having fins disposed on heat transfer tubes.
Background
There are heat exchangers in which cut-in portions, cut-out portions, or heat transfer promoting portions as louvers are provided on heat transfer plates constituting fins provided on a heat transfer tube. The heat transfer pipes are provided with heat transfer plates on the windward side and the leeward side, respectively, and the heat transfer promoting portion is provided on the windward side of the heat exchange member (for example, refer to patent document 1).
Prior art literature
Patent literature
Patent document 1: international publication No. 2019/026243 (see FIG. 18)
Disclosure of Invention
Problems to be solved by the invention
However, in the fin disclosed in patent document 1, the problem is that air is not allowed to leave a heat transfer promoting portion with high pressure loss of a heat transfer plate placed on the windward side, air flow is concentrated on a flat portion of the heat transfer plate, and heat transfer rate between the air and the fin is insufficient.
The present disclosure has been made in view of the above-described circumstances, and an object thereof is to provide a heat exchanger having fins capable of improving heat transfer rate between gas and fins.
Means for solving the problems
The heat exchanger of the present disclosure has: a heat transfer pipe extending in a2 nd direction intersecting the 1 st direction of the gas flow; and a fin provided to the heat transfer tube and having a surface along the 1 st and 2 nd directions, the fin including: a1 st extension portion provided on an upstream side of the heat transfer pipe with respect to the gas in the 1 st direction, the extension portion having a1 st heat transfer promoting region for improving a heat transfer rate; and a2 nd extension portion provided downstream of the heat transfer pipe with respect to the gas in the 1 st direction, the extension portion having a2 nd heat transfer promoting region for improving a heat transfer rate.
Effects of the invention
According to the present disclosure, the 1 st heat transfer promoting region is provided in the 1 st extension portion of the fin provided on the upstream side of the gas, and the 2 nd heat transfer promoting region is provided in the 2 nd extension portion of the fin provided on the downstream side of the 1 st extension portion of the fin. Accordingly, a heat exchanger can be provided in which the heat transfer rate between the fins and the gas passing through the fins can be improved by the 1 st heat transfer promoting region and the 2 nd heat transfer promoting region.
Drawings
Fig. 1 is a schematic configuration diagram illustrating a refrigeration cycle apparatus according to embodiment 1.
Fig. 2 is a perspective view illustrating the outdoor heat exchanger of fig. 1.
Fig. 3 is a diagram showing a heat transfer member of the heat exchanger of embodiment 1.
Fig. 4 is a diagram showing a modification of the mounting method of the fins of the heat exchanger according to embodiment 1 to the heat transfer tube.
Fig. 5 is a diagram showing a heat transfer member of the heat exchanger of embodiment 2.
Fig. 6 is a diagram showing a heat transfer member of the heat exchanger of embodiment 3.
Fig. 7 is a diagram showing a heat transfer member of the heat exchanger according to embodiment 4.
Fig. 8 is a diagram showing a modification of the heat transfer member of the heat exchanger according to embodiment 4.
Fig. 9 is a diagram showing a heat exchange member of the heat exchanger according to embodiment 5.
Fig. 10 is a diagram showing a modification of the heat exchange member of the heat exchanger according to embodiment 5.
Fig. 11 is a diagram showing the arrangement of the 1 st heat transfer promoting portion and the 2 nd heat transfer promoting portion formed on the fin of the comparative example.
Fig. 12 is a graph showing a relationship between the gap area ratio and the air-side heat transfer performance.
Detailed Description
An air conditioner according to an embodiment will be described below with reference to the drawings. In the drawings, the same components are denoted by the same reference numerals, and the description is repeated only when necessary. The present disclosure can include all combinations of the combinable structures among the structures described in the embodiments below. In the drawings, the relationship between the sizes of the respective structural members may be different from the actual ones. The form of the constituent elements shown throughout the specification is merely an example, and is not limited to the form described in the specification. In particular, the combination of the components is not limited to the combination in each embodiment, and the components described in other embodiments can be applied to different embodiments. In the following embodiments, a plurality of components may be provided, and the components may be distinguished from each other by underlining and numbering at the end of the reference numerals of the components. However, when a plurality of these components are collectively described or when 1 of these components is described as a representative, the description may be made without adding an underline or a number.
Embodiment 1
Fig. 1 is a schematic configuration diagram illustrating a refrigeration cycle apparatus according to embodiment 1. In embodiment 1, a refrigeration cycle apparatus is used as the air conditioner 1. The air conditioner 1 has a compressor 2, an outdoor heat exchanger 3, an expansion valve 4, an indoor heat exchanger 5, and a four-way valve 6. In this example, the compressor 2, the outdoor heat exchanger 3, the expansion valve 4, and the four-way valve 6 are provided in an outdoor unit, and the indoor heat exchanger 5 is provided in an indoor unit.
The compressor 2, the outdoor heat exchanger 3, the expansion valve 4, the indoor heat exchanger 5, and the four-way valve 6 are connected to each other via refrigerant pipes, thereby constituting a refrigerant circuit capable of circulating a refrigerant. In the air conditioner 1, the compressor 2 is operated, and thereby a refrigeration cycle is performed in which the refrigerant circulates through the compressor 2, the outdoor heat exchanger 3, the expansion valve 4, and the indoor heat exchanger 5 while undergoing a phase change.
The outdoor unit is provided with an outdoor fan 7 for forcibly passing the outdoor air through the outdoor heat exchanger 3. The outdoor heat exchanger 3 exchanges heat between the flow of outdoor air generated by the operation of the outdoor fan 7 and the refrigerant. The indoor unit is provided with an indoor fan 8 for forcibly passing indoor air through the indoor heat exchanger 5. The indoor heat exchanger 5 exchanges heat between the flow of indoor air generated by the operation of the indoor fan 8 and the refrigerant.
The operation of the air conditioner 1 can be switched between the cooling operation and the heating operation. The four-way valve 6 is a solenoid valve that switches the refrigerant flow path according to switching between the cooling operation and the heating operation of the air conditioner 1. The four-way valve 6 guides the refrigerant from the compressor 2 to the outdoor heat exchanger 3 and guides the refrigerant from the indoor heat exchanger 5 to the compressor 2 during the cooling operation, guides the refrigerant from the compressor 2 to the indoor heat exchanger 5 and guides the refrigerant from the outdoor heat exchanger 3 to the compressor 2 during the heating operation. In fig. 1, the direction of the flow of the refrigerant during the cooling operation is shown by the arrow of the broken line, and the direction of the flow of the refrigerant during the heating operation is shown by the arrow of the solid line.
During cooling operation of the air conditioner 1, the refrigerant compressed by the compressor 2 is sent to the outdoor heat exchanger 3. In the outdoor heat exchanger 3, the refrigerant releases heat to the outdoor air to be condensed. The refrigerant is sent to the expansion valve 4, depressurized by the expansion valve 4, and then sent to the indoor heat exchanger 5. Then, the refrigerant is evaporated by taking heat from the indoor air in the indoor heat exchanger 5, and is returned to the compressor 2. Therefore, during the cooling operation of the air conditioner 1, the outdoor heat exchanger 3 functions as a condenser and the indoor heat exchanger 5 functions as an evaporator.
During the heating operation of the air conditioner 1, the refrigerant compressed by the compressor 2 is sent to the indoor heat exchanger 5. In the indoor heat exchanger 5, the refrigerant releases heat to the indoor air to be condensed. The refrigerant is sent to the expansion valve 4, depressurized by the expansion valve 4, and then sent to the outdoor heat exchanger 3. Then, the refrigerant is evaporated by taking heat from the outdoor air in the outdoor heat exchanger 3, and is returned to the compressor 2. Therefore, during the heating operation of the air conditioner 1, the outdoor heat exchanger 3 functions as an evaporator, and the indoor heat exchanger 5 functions as a condenser.
Fig. 2 is a perspective view illustrating the outdoor heat exchanger 3 of fig. 1. The outdoor heat exchanger 3 has a heat exchanger 11 through which an air flow a generated by the operation of the outdoor fan 7 passes. The heat exchanger 11 has a 1 st header tank 12, a2 nd header tank 13, and a plurality of heat exchange members 14 connected between the 1 st header tank 12 and the 2 nd header tank 13. In the heat exchanger 11, one of the refrigerant pipe from the expansion valve 4 and the refrigerant pipe from the four-way valve 6 is connected to the 1 st header tank 12, and the other is connected to the 2 nd header tank 13.
The 1 st header tank 12 and the 2 nd header tank 13 are respectively horizontally arranged. The 2 nd header tank 13 is disposed above the 1 st header tank 12. The 1 st header tank 12 and the 2 nd header tank 13 are arranged parallel to each other along the z direction of fig. 2 as the 3 rd direction.
In fig. 2, the 1 st header tank 12 and the 2 nd header tank 13 are rectangular parallelepiped in shape, but the shape is not limited. The outer shape of the 1 st header tank 12 and the 2 nd header tank 13 may be, for example, a cylinder, an elliptic cylinder, or the like, and the cross-sectional shape may be appropriately changed. The 1 st header tank 12 and the 2 nd header tank 13 may be constructed by stacking, for example, a tubular body having both ends closed, a plate-like body having a slit 21 formed therein, or the like. The 1 st header tank 12 and the 2 nd header tank 13 are each formed with a refrigerant flow port through which a refrigerant flows out and in.
The plurality of heat exchange members 14 are arranged at intervals in the longitudinal direction of each of the 1 st header tank 12 and the 2 nd header tank 13, that is, in the z-direction of fig. 2. Further, the plurality of heat exchange members 14 are arranged in parallel with each other. The longitudinal direction of the plurality of heat exchange members 14 is the y-direction intersecting the z-direction of fig. 2 as the 2 nd direction. In the present embodiment, the y direction is the up-down direction. In this example, the longitudinal direction of each heat exchange member 14 is perpendicular to the longitudinal direction of each of the 1 st header tank 12 and the 2 nd header tank 13. Further, in this example, the space arrangement members between the plurality of heat exchange members 14 are prohibited. In this way, in this example, the connection members are prevented from being connected to the surfaces of the heat exchange members 14 adjacent to each other that face each other.
The air flow a generated by the operation of the outdoor fan 7 passes between the plurality of heat exchange members 14. In this example, the air flow a passes between the plurality of heat exchange members 14 in a direction intersecting the longitudinal direction of each of the 1 st header tank 12, the 2 nd header tank 13, and the heat exchange members 14, that is, in the x direction, which is the 1 st direction, in fig. 2. In the example of fig. 2, the x-direction is perpendicular to the y-direction, which is the longitudinal direction of the heat exchange member 14.
Fig. 3 is a diagram showing the heat exchange member 14 of the heat exchanger 11 according to embodiment 1. Fig. 3 is a view of the heat exchange member 14 shown in fig. 2 viewed in the z direction. In fig. 3, white arrows show the direction of gas flow. Fig. 3 shows 1 heat exchange member 14 as an example among the plurality of heat exchange members 14 shown in fig. 2.
The heat exchange member 14 has heat transfer pipes 15 and fins 16.
As shown in fig. 2, the heat transfer tubes 15 are arranged at predetermined intervals in the z-direction. The heat transfer pipe 15 is a round pipe or a flat pipe. Further, as shown in fig. 3, the heat transfer pipe 15 extends in the y-direction, connecting the 1 st header tank 12 and the 2 nd header tank 13. The heat transfer pipe 15 extends in the y direction, i.e., in the up-down direction, and the refrigerant flowing into the heat transfer pipe 15 from the 1 st header tank 12 or the 2 nd header tank 13 flows in the up-down direction in the heat transfer pipe 15.
As shown in fig. 3, the fins 16 have faces along the x-direction and the y-direction. The fins 16 are provided on the heat transfer pipe 15 so that the longitudinal direction thereof extends along the y-direction. The fin 16 has a1 st extension 16_1 and a 2 nd extension 16_2.
The 1 st extension portion 16_1 and the 2 nd extension portion 16_2 are located outside the heat transfer pipe 15 in the x-direction. In the example of fig. 3, the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 are the same size and are provided to the heat transfer pipe 15 so that the longitudinal direction thereof extends along the y-direction. The 1 st extension portion 16_1 and the 2 nd extension portion 16_2, which are separately configured, are attached to sides of the heat transfer tube 15 in the y direction, respectively.
When viewed from the z direction, the 1 st extension portion 16_1 has a rectangular shape, and one of the long sides thereof is provided to the heat transfer pipe 15. The 1 st extension 16_1 has a short side extending upward in the x direction. The 1 st extension portion 16_1 is provided on the upstream side of the gas passing through the fins 16, and has a 1 st heat transfer promoting region 17_1 that increases the heat transfer rate between the gas and the 1 st extension portion 16_1.
The 1 st heat transfer promoting region 17_1 is provided on the upstream side of the gas passing through the fins 16, and has a plurality of 1 st heat transfer promoting portions 17_1_1 that increase the heat transfer rate between the gas and the 1 st extension portion 16_1. The plurality of 1 st heat transfer promoting portions 17_1_1 are arranged along the y direction. The 1 st heat transfer promoting region 17_1 has a1 st flat portion 17_1_2, and the 1 st flat portion 17_1_2 is located between the 1 st heat transfer promoting portion 17_1_1 arranged on the upper side with respect to the y direction and the 1 st heat transfer promoting portion 17_1_1 arranged on the lower side. In the example of fig. 3, the 1 st flat portion 17_1_2 is provided in the 1 st heat transfer promoting region 17_1. The 1 st heat transfer promoting portions 17_1_1 and the 1 st flat portions 17_1_2 are alternately arranged along the y direction.
The 1 st heat transfer promoting portion 17_1_1 has 3 slits 21 arranged in parallel along the x direction. The slit 21 is an opening penetrating the fin 16. Instead of the slit 21 of the 1 st heat transfer promoting portion 17_1_1, a cut-and-raised portion, a louver, or a concave-convex portion may be provided. The cut-and-raised portion is formed by raising a portion between 2 parallel slit-like slits formed in the surface of the fin 16 in the z-direction. As a result of the formation of the cut-and-raised portions, openings having the same shape as the cut-and-raised portions are formed in the fins 16. The cut-and-raised portion protrudes from the fin 16 facing in the z-direction. The louver is formed by inclining a portion between 2 slits formed in the surface of the fin 16 with respect to the surface of the fin 16. As a result of the formation of the louver, openings having the same shape as the louver are formed in the fins 16. The concave-convex portion is formed by projecting or recessing the surface of the fin 16 in the z direction. In the same manner as in embodiment 2 and the following, the 1 st heat transfer promoting portion 17_1_1 may be a cut-up portion, a louver, or a concave-convex portion.
The 1 st flat portion 17_1_2 is a flat rectangular-shaped region between the 1 st heat transfer promoting portions 17_1_1 of the fins 16. The length of the 1 st flat portion 17_1_2 in the y direction is shorter than the length of the 1 st heat transfer promoting portion 17_1_1 in the y direction.
When viewed in the z direction, the 2 nd extension portion 16_2 has a rectangular shape, and one of the long sides thereof is provided to the heat transfer pipe 15. The short side of the 2 nd extension portion 16_2 is disposed so as to extend downstream in the x direction. The 2 nd extension portion 16_2 is provided on the downstream side of the gas passing through the fin 16, and has a2 nd heat transfer promoting region 17_2 that increases the heat transfer rate between the gas and the 2 nd extension portion 16_2.
The 2 nd heat transfer promoting region 17_2 is provided on the downstream side of the gas passing through the fins 16, and has a plurality of 2 nd heat transfer promoting portions 17_2_1 that increase the heat transfer rate between the gas and the 2 nd extension portions 16_2. The plurality of 2 nd heat transfer promoting portions 17_2_1 are arranged along the y direction. The 2 nd heat transfer promoting region 17_2 has a 2 nd flat portion 17_2_2, and the 2 nd flat portion 17_2_2 is located between the 2 nd heat transfer promoting portion 17_2_1 arranged on the upper side in the y direction and the 2 nd heat transfer promoting portion 17_2_1 arranged on the lower side. In the example of fig. 3, the 2 nd flat portions 17_2_2 are provided in the 2 nd heat transfer promoting region 17_2. The 2 nd heat transfer promoting portions 17_2_1 and the 2 nd flat portions 17_2_2 are alternately arranged along the y direction.
The 2 nd heat transfer promoting portion 17_2_1 has 3 slits 21 arranged in parallel along the x direction. The slit 21 is an opening penetrating the fin 16. Instead of the slit 21 of the 2 nd heat transfer promoting portion 17_2_1, a cut-up portion, a louver, or a concave-convex portion may be provided. The cut-and-raised portion is formed by raising a portion between 2 parallel slit-like slits formed in the surface of the fin 16 in the z-direction. As a result of the formation of the cut-and-raised portions, openings having the same shape as the cut-and-raised portions are formed in the fins 16. The cut-and-raised portion protrudes from the fin 16 facing in the z-direction. The louver is formed by inclining a portion between 2 slits formed in the surface of the fin 16 with respect to the surface of the fin 16. As a result of the formation of the louver, openings having the same shape as the louver are formed in the fins 16. The concave-convex portion is formed by projecting or recessing the surface of the fin 16 in the z direction. In the same manner as in embodiment 2 and the following, the 2 nd heat transfer promoting portion 17_2_1 may be a cut-up portion, a louver, or a concave-convex portion.
The 2 nd flat portion 17_2_2 is a flat rectangular-shaped region between the 2 nd heat transfer promoting portions 17_2_1 of the fins 16. The length of the 2 nd flat portion 17_2_2 in the y direction is shorter than the length of the 2 nd heat transfer promoting portion 17_2_1 in the y direction.
In the x-direction, the 2 nd flat portion 17_2_2 is arranged in the 2 nd heat transfer promoting region 17_2 on the gas downstream side of the 1 st heat transfer promoting portion 17_1_1, and the 2 nd heat transfer promoting portion 17_2_1 is arranged in the 2 nd heat transfer promoting region 17_2 on the gas downstream side of the 1 st flat portion 17_1_2. That is, the heat exchange member 14 has a region in which the 1 st heat transfer promoting portion 17_1_1 and the 2 nd flat portion 17_2_2 are juxtaposed in the x direction, and a region in which the 1 st flat portion 17_1_2 and the 2 nd heat transfer promoting portion 17_2_1 are juxtaposed in the x direction. Further, in the example of fig. 3, a region is provided in which the 1 st heat transfer promoting portion 17_1_1 and the 2 nd heat transfer promoting portion 17_2_1 are juxtaposed in the x direction.
In the heat exchanger 11 of embodiment 1, the inflowing air flow flows in the x direction on the surface of the 1 st heat transfer promoting region 17_1 of the fin 16. In the 1 st heat transfer promoting region 17_1, a part of the airflow promotes heat transfer in the slit 21 formed in the 1 st heat transfer promoting portion 17_1_1. In addition, the air flow flowing into the 1 st flat portion 17_1_2 and the other air flows avoiding the 1 st heat transfer promoting portion 17_1_1 flow in the x direction on the surface of the 1 st flat portion 17_1_2.
Then, the air flow passes through the surface of the heat transfer pipe 15, exchanges heat with the refrigerant flowing through the heat transfer pipe 15, and then flows in the x direction on the surface of the 2 nd heat transfer promoting region 17_2. In the 2 nd heat transfer promoting region 17_2, a part of the airflow promotes heat transfer in the slit 21 formed in the 2 nd heat transfer promoting portion 17_2_1. In addition, the air flow flowing into the 2 nd flat portion 17_2_2 and the other air flows avoiding the 2 nd heat transfer promoting portion 17_2_1 flow in the x direction on the surface of the 2 nd flat portion 17_2_2.
Fig. 4 is a diagram showing a modification of the mounting method of the fins 16 of the heat exchanger 11 to the heat transfer pipe 15 according to embodiment 1. Fig. 4 is a view of the heat transfer pipe 15 and the fins 16 viewed in the y direction. In the above description, the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 of the fin 16 are each attached to the heat transfer tube 15, but as shown in fig. 4, the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 may be integrally formed. The same applies to other embodiments 2,3, 4 and 5.
The fin 16 has a 1 st extension portion 16_1, a2 nd extension portion 16_2, and a main body portion 16_3. The 1 st extension portion 16_1 and the 2 nd extension portion 16_2 of the fin 16 shown in fig. 4 are integrally formed together with the main body portion 16_3. The main body portion 16_3 is bent so as to be in contact with the heat transfer tube 15, and the bent main body portion 16_3 is attached to the heat transfer tube 15. The heat exchange member 14 of the present embodiment can be constituted by such a mounting form.
Further, the positions of the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 with respect to the heat transfer pipe 15 in the z direction can be constituted as follows. For example, as shown in fig. 4, the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 are arranged in parallel with the center of the heat transfer tube 15 in the z direction. This configuration can also be applied to a form in which the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 are individually mounted to the heat transfer tube 15. The 1 st extension portion 16_1 and the 2 nd extension portion 16_2 may not be strictly juxtaposed with the center of the heat transfer tube 15 in the z direction, and the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 may be disposed within the range of the heat transfer tube 15 in the z direction. Although not shown, the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 may be arranged coplanar with the end surface of the heat transfer tube 15 in the z direction.
As described above, the heat exchanger 11 of embodiment 1 includes: a heat transfer pipe 15 extending in a2 nd direction intersecting the 1 st direction of the gas flow; and a fin 16 provided to the heat transfer pipe 15 and having a surface along the 1 st and 2 nd directions. The fins 16 have 1 st extending portions 16_1, and the 1 st extending portions 16_1 are provided on the upstream side of the heat transfer tube 15 in the 1 st direction, and have 1 st heat transfer promoting regions 17_1 for improving the heat transfer rate with the gas. The fin 16 has a2 nd extension portion 16_2, and the 2 nd extension portion 16_2 is provided on the downstream side of the heat transfer tube 15 in the 1 st direction, and has a2 nd heat transfer promoting region 17_2 for improving the heat transfer rate with the gas. The heat exchanger 11 according to embodiment 1 is provided with the 1 st heat transfer promoting region 17_1 on the upstream side and the 2 nd heat transfer promoting region 17_2 on the downstream side of the heat transfer tubes 15, and therefore, the heat transfer rate between the fins 16 and the gas passing through the fins 16 can be improved.
Here, when the gas is sent toward the heat transfer pipe 15, the gas flows around the surface of the heat transfer pipe 15 along the x-direction so as to bypass the heat transfer pipe 15, and the gas does not easily flow toward the upstream end and the downstream end (the left and right end of the paper surface of the heat transfer pipe 15 illustrated in fig. 4) of the heat transfer pipe 15 in the gas flow direction. However, in the present embodiment, the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 extending in the x-direction of the gas flow are provided on the upstream side and the downstream side of the heat transfer tube 15, respectively. The 1 st extension portion 16_1 is provided with a1 st heat transfer promoting region 17_1 for improving the heat transfer rate with the gas, and the 2 nd extension portion 16_2 is provided with a 2 nd heat transfer promoting region 17_2 for improving the heat transfer rate with the gas. Therefore, the heat transfer rate between the fin 16 and the gas flowing in the x direction can be improved.
The 2 nd flat portion 17_2_2 is disposed in the 2 nd heat transfer promoting region 17_2 juxtaposed in the x direction with the 1 st heat transfer promoting portion 17_1_1, and the 2 nd heat transfer promoting portion 17_2_1 is disposed in the 2 nd heat transfer promoting region 17_2 juxtaposed in the x direction with the 1 st flat portion 17_1_2. Therefore, even if the gas flowing in the x-direction flows in the 1 st flat portion 17_1_2 on the upstream side, the gas easily flows in the 2 nd heat transfer promoting portion 17_2_1 on the downstream side thereof. Further, the gas flowing in the 1 st flat portion 17_1_2 on the downstream side flows around the 1 st heat transfer promoting portion 17_1_1 on the upstream side thereof. Therefore, the heat transfer rate in the fins 16 can be improved. Further, according to this structure, the path of the air flow passing through the 1 st flat portion 17_1_2 or the 2 nd flat portion 17_2_2 through the entire fin 16 can be extended, and therefore, the substantial heat transfer area in the fin 16 can be enlarged.
In the 1 st heat transfer promoting region 17_1, the 1 st heat transfer promoting portions 17_1_1 and the 1 st flat portions 17_1_2 are alternately arranged along the y direction, which is the 2 nd direction. In the 2 nd heat transfer promoting region 17_2, the 2 nd heat transfer promoting portions 17_2_1 and the 2 nd flat portions 17_2_2 are alternately arranged along the y direction, which is the 2 nd direction. Therefore, when the pressure loss distribution of the entire fin 16 is observed, the pressure loss distribution of the air flow in the y direction is nearly uniform. Therefore, as a result of the decrease in the air flow passing through the 1 st flat portion 17_1_2 and the 2 nd flat portion 17_2_2, the heat transfer rate between the air flow and the fins 16 increases.
Embodiment 2
The heat exchange member 14 of the heat exchanger 11 according to embodiment 2 is different in size between the 1 st flat portion 17_1_2 and the 1 st flat portion 17_1_2 from the heat exchange member 14 of the heat exchanger 11 according to embodiment 1.
Fig. 5 is a diagram showing the heat exchange member 14 of the heat exchanger 11 according to embodiment 2. In fig. 5, white arrows show the direction of the gas flow. In fig. 5, 1 heat exchange member 14 is shown as an example among the plurality of heat exchange members 14 shown in fig. 2.
As shown in fig. 5, in embodiment 2, the lengths in the x-direction and the y-direction of the 1 st heat transfer promoting portion 17_1_1, the 1 st flat portion 17_1_2, the 2 nd heat transfer promoting portion 17_2_1, and the 2 nd flat portion 17_2_2 are the same. In addition, only the 1 st heat transfer promoting portion 17_1_1, the 1 st flat portion 17_1_2, and the 2 nd heat transfer promoting portion 17_2_1 and the 2 nd flat portion 17_2_2 may have the same length in the y direction.
The position of the 1 st heat transfer promoting portion 17_1_1 in the y direction is the same as the position of the 2 nd flat portion 17_2_2 in the 2 nd heat transfer promoting region 17_2 in the y direction. The position of the 1 st flat portion 17_1_2 in the y direction is the same as the position of the 2 nd heat transfer promoting portion 17_2_1 in the y direction in the 2 nd heat transfer promoting region 17_2.
That is, the positions of the 1 st heat transfer promoting portion 17_1_1 and the 2 nd heat transfer promoting portion 17_2_1 formed on the fin 16 of the heat exchanger 11 of embodiment 2 are shifted from each other in the y direction. Also, the positions of the 1 st flat portion 17_1_2 and the 2 nd flat portion 17_2_2 are offset from each other in the y direction.
As described above, the heat exchanger 11 according to embodiment 2 includes: a heat transfer pipe 15 extending in a 2 nd direction intersecting the 1 st direction of the gas flow; and a fin 16 provided to the heat transfer pipe 15 and having a surface along the 1 st and 2 nd directions. The fins 16 have 1 st extending portions 16_1, and the 1 st extending portions 16_1 are provided on the upstream side of the heat transfer tube 15 in the 1 st direction, and have 1 st heat transfer promoting regions 17_1 for improving the heat transfer rate with the gas. The fin 16 has a 2 nd extension portion 16_2, and the 2 nd extension portion 16_2 is provided on the downstream side of the heat transfer tube 15 in the 1 st direction, and has a 2 nd heat transfer promoting region 17_2 for improving the heat transfer rate with the gas. The heat exchanger 11 according to embodiment 1 is provided with the 1 st heat transfer promoting region 17_1 on the upstream side and the 2 nd heat transfer promoting region 17_2 on the downstream side of the heat transfer tubes 15, and therefore, the heat transfer rate between the fins 16 and the gas passing through the fins 16 can be improved.
Here, when the gas is sent toward the heat transfer pipe 15, the gas flows around the surface of the heat transfer pipe 15 along the x-direction so as to bypass the heat transfer pipe 15, and the gas does not easily flow toward the upstream end and the downstream end (the left and right end of the paper surface of the heat transfer pipe 15 illustrated in fig. 4) in the gas flow direction of the heat transfer pipe 15. However, in the present embodiment, the 1 st extension portion 16_1 and the 2 nd extension portion 16_2 extending in the x-direction of the gas flow are provided on the upstream side and the downstream side of the heat transfer tube 15, respectively. The 1 st extension portion 16_1 is provided with a1 st heat transfer promoting region 17_1 for improving the heat transfer rate with the gas, and the 2 nd extension portion 16_2 is provided with a2 nd heat transfer promoting region 17_2 for improving the heat transfer rate with the gas. Therefore, the heat transfer rate between the fin 16 and the gas flowing in the x direction can be improved.
In embodiment 2, the lengths of the 1 st heat transfer promoting portion 17_1_1, the 1 st flat portion 17_1_2, and the 2 nd heat transfer promoting portion 17_2_1 and the 2 nd flat portion 17_2_2 in the x-direction and the y-direction are the same. Therefore, in manufacturing the fin 16, the 1 st heat transfer promoting portion 17_1 and the 2 nd heat transfer promoting portion 17_2_1 can be formed on the fin 16 by feeding and punching in order.
Embodiment 3
The heat exchange member 14 of the heat exchanger 11 of embodiment 3 does not have the 1 st flat portion 17_1_2 and the 2 nd flat portion 17_2_2 provided in the heat exchange member 14 of the heat exchanger 11 of embodiment 1.
Fig. 6 is a diagram showing the heat exchange member 14 of the heat exchanger 11 according to embodiment 3. In fig. 6, white arrows show the direction of the gas flow. In fig. 6, 1 heat exchange member 14 is shown as an example among the plurality of heat exchange members 14 shown in fig. 2.
As shown in fig. 6, in embodiment 3, the 1 st heat transfer promoting region 17_1 has a plurality of 1 st heat transfer promoting portions 17_1_1 which are arranged along the y direction and which increase the heat transfer rate with the gas. The 2 nd heat transfer promoting region 17_2 has a plurality of 2 nd heat transfer promoting portions 17_2_1 arranged along the y-direction and improving the heat transfer rate with the gas.
The 1 st heat transfer promoting portion 17_1_1 has 1 slit 21. The positions of the slits 21 provided in the 1 st heat transfer promoting portion 17_1_1 adjacent in the y direction are different from each other in the x direction. The plurality of slits 21 formed in the 1 st heat transfer promoting portion 17_1_1 may be formed along the x direction.
In the 1 st extension portion 16_1, as shown in fig. 6, 3 slits 21 are formed in sequence in the y direction at different positions in the x direction, and the pattern thereof is repeated.
The 2 nd heat transfer promoting portion 17_2_1 has 1 slit 21. The positions of the slits 21 provided in the 2 nd heat transfer promoting portion 17_2_1 adjacent in the y direction are different from each other in the x direction. A plurality of slits 21 may be formed in the 2 nd heat transfer promoting portion 17_2_1 along the x direction.
In the 2 nd extension portion 16_2, as shown in fig. 6, 3 slits 21 are formed in sequence in the y direction at different positions in the x direction, and the pattern thereof is repeated.
In embodiment 3, the sum of the number of slits 21 formed in the 1 st heat transfer promoting portion 17_1_1 in the x direction and the number of slits 21 formed in the 2 nd heat transfer promoting portion 17_2_1 in the x direction is fixed.
According to embodiment 3, a plurality of 1 st heat transfer promoting portions 17_1_1 and 2 nd heat transfer promoting portions 17_2_1 are provided along the y direction of the fins 16. Further, the sum of the number of slits 21 formed in the 1 st heat transfer promoting portion 17_1_1 in the x direction and the number of slits 21 formed in the 2 nd heat transfer promoting portion 17_2_1 in the x direction is fixed. That is, the slits 21 provided in the x-direction by the same number (2 in the example of fig. 6) are arranged in plural groups along the y-direction. Therefore, the pressure loss distribution in the y direction of the airflow can be made uniform. This improves the heat transfer rate of the fins 16 of the heat exchanger 11.
Embodiment 4
In the heat exchange member 14 of the heat exchanger 11 according to embodiment 4, the 1 st pattern formed in the arrangement of the slits 21 of the 1 st heat transfer promoting portion 17_1_1 and the 2 nd pattern formed in the arrangement of the slits 21 of the 2 nd heat transfer promoting portion 17_2_1 are offset in the x direction.
Fig. 7 is a diagram showing the heat exchange member 14 of the heat exchanger 11 according to embodiment 4. In fig. 7, white arrows show the direction of the gas flow. In fig. 7, 1 heat exchange member 14 is shown as an example among the plurality of heat exchange members 14 shown in fig. 2.
As shown in fig. 7, in embodiment 4, the 1 st heat transfer promoting region 17_1 has a plurality of 1 st heat transfer promoting portions 17_1_1 which are arranged along the y direction and which increase the heat transfer rate with the gas. The 2 nd heat transfer promoting region 17_2 has a plurality of 2 nd heat transfer promoting portions 17_2_1 arranged along the y-direction and improving the heat transfer rate with the gas.
A1 st pattern of slits 21 is formed in the plurality of 1 st heat transfer promoting portions 17_1_1. The 1 st pattern is a pattern in which 2 slits 21 juxtaposed in the x direction and 1 slit 21 provided adjacent to the 2 slits 21 in the y direction in the 1 st heat transfer promoting portion 17_1_1 are continuous in the y direction. In the example of fig. 7, 1 slit 21 adjacent in the y direction is arranged at a position intermediate 2 slits juxtaposed in the x direction.
A2 nd pattern of slits 21 is formed in the plurality of 2 nd heat transfer promoting portions 17_2_1. The 2 nd pattern is a pattern in which 1 slit 21 in the x direction and 2 slits 21 arranged on both sides of the 1 slit 21 at the lower part of the 1 slit 21 in the y direction are continuous in the y direction in the 2 nd heat transfer promoting portion 17_2_1.
As shown in fig. 7, the arrangement of the 1 st pattern and the 2 nd pattern slits 21 is shifted in the y direction. When viewed in the x-direction, the sum of the number of slits 21 formed in the 1 st heat transfer promoting portion 17_1_1 and the number of slits 21 formed in the 2 nd heat transfer promoting portion 17_2_1 is fixed to 3.
The 1 st pattern and the 2 nd pattern are not limited to the example shown in fig. 7, and various numbers of patterns of the slits 21 can be adopted. For example, a pattern in which a group of 3 slits 21 juxtaposed in the x-direction and only 1 slit 21 arranged in the x-direction is repeatedly arranged in the y-direction is provided.
Fig. 8 is a diagram showing a modification of the heat exchange member 14 of the heat exchanger 11 according to embodiment 4.
As shown in fig. 8, the 1 st flat portion 17_1_2 is arranged at the y-direction lower portion of the 1 st heat transfer promoting portion 17_1_1. The 1 st heat transfer promoting portion 17_1_1 is arranged in the y direction with the 1 st flat portion 17_1_2 interposed therebetween.
A1 st pattern of square-shaped concave-convex portions 22 is formed in the plurality of 1 st heat transfer promoting portions 17_1_1. The 1 st pattern is a pattern in which 2 concave-convex portions 22 juxtaposed in the x direction and 1 concave-convex portion 22 provided adjacent to the 2 concave-convex portions 22 in the y direction in the 1 st heat transfer promoting portion 17_1_1 are continuous in the y direction across the 1 st flat portion 17_1_2.
A2 nd pattern of square-shaped concave-convex portions 22 is formed in the plurality of 2 nd heat transfer promoting portions 17_2_1. The 2 nd pattern is a pattern in which 2 concave-convex portions 22 arranged in parallel in the x direction in the 2 nd heat transfer promoting portion 17_2_1 and 1 concave-convex portion 22 arranged in the y direction lower portion between the 2 concave-convex portions 22 are continuous in the y direction across the 2 nd flat portion 17_2_2.
In fig. 8, the arrangement of the concave-convex portions 22 of the 1 st pattern and the 2 nd pattern is also shifted in the y direction, which is the 2 nd direction. When viewed from the x-direction, the sum of the number of concave-convex portions 22 formed in the 1 st heat transfer promoting portion 17_1_1 and the number of concave-convex portions 22 formed in the 2 nd heat transfer promoting portion 17_2_1 is fixed to 3.
In fig. 8, the 1 st flat portion 17_1_2 and the 2 nd flat portion 17_2_2 may be omitted.
As described above, according to embodiment 4, the 1 st pattern of the arrangement of the slits or projections and depressions provided in the 1 st heat transfer promoting portion and the 2 nd pattern of the slits or projections and depressions provided in the 2 nd heat transfer promoting portion are shifted in the 2 nd direction. Therefore, the pressure loss distribution of the air flow in the y direction can be reduced. This improves the heat transfer rate of the fins 16 of the heat exchanger 11.
Further, by shifting the 1 st pattern of the 1 st heat transfer promoting portion 17_1_1 and the 2 nd pattern of the 2 nd heat transfer promoting portion 17_2_1, the 1 st pattern and the 2 nd pattern can be formed by feeding punching in sequence.
Embodiment 5
Next, the heat exchanger 11 according to embodiment 5 will be described.
Fig. 9 is a diagram showing the heat exchange member 14 of the heat exchanger 11 according to embodiment 5. In fig. 9, white arrows show the direction of the gas flow. In fig. 9, the plurality of heat exchange members 14 shown in fig. 2 are provided with at least 2 columns in the x-direction, wherein, as an example, a column 1 heat exchange member 14_1 and a column 2 heat exchange member 14_2 are shown.
As shown in fig. 9, the fins 16 are provided in the 1 st heat transfer tube 15_1 along the y-direction, which is the vertical direction. The 1 st heat transfer pipe 15_1 is provided between the 1 st header tank 12_1 and the 2 nd header tank 13_1. The fin 16 has a1 st extension 16_1 and a2 nd extension 16_2.
The 1 st extension portion 16_1 of the fin 16 has a rectangular shape, one of the long sides is attached to the 1 st heat transfer tube 15_1 in the y direction, and the short side is disposed so as to extend upward in the x direction.
The 2 nd extension portion 16_2 of the fin 16 has a rectangular shape, one of the long sides is attached to the 1 st heat transfer tube 15_1 in the y direction, and the short side is disposed so as to extend downstream in the x direction.
The 1 st extension 16_1 is provided on the upstream side of the gas passing through the fin 16. When viewed from the z direction, the 1 st extension portion 16_1 has a rectangular shape, and the long side thereof is provided in the 1 st heat transfer tube 15_1. The 1 st extension portion 16_1 is provided with a1 st heat transfer promoting region 17_1 that increases the heat transfer rate between the 1 st extension portion 16_1 and the gas. The 1 st heat transfer promoting region 17_1 includes a plurality of 1 st heat transfer promoting portions 17_1_1 arranged along the y-direction and improving the heat transfer rate with the gas, and a plurality of 1 st flat portions 17_1_2 arranged along the y-direction. The 1 st heat transfer promoting portions 17_1_1 and the 1 st flat portions 17_1_2 are alternately arranged along the y direction.
In the 1 st heat transfer promoting portion 17_1_1, 3 slits 21 are arranged in parallel in the x direction. The 1 st flat portion 17_1_2 is a flat rectangular-shaped region between the 1 st heat transfer promoting portions 17_1_1 of the fins 16. The length of the 1 st flat portion 17_1_2 in the y direction is the same as the length of the 1 st heat transfer promoting portion 17_1_1 in the y direction.
The 2 nd extension 16_2 is provided on the downstream side of the gas passing through the fin 16. When viewed from the z direction, the 2 nd extension portion 16_2 has a rectangular shape, and the long side thereof is provided in the 1 st heat transfer tube 15_1. The 2 nd extension portion 16_2 is provided with a2 nd heat transfer promoting region 17_2 that increases the heat transfer rate between the 2 nd extension portion 16_2 and the gas. The 2 nd heat transfer promoting region 17_2 includes a plurality of 2 nd heat transfer promoting portions 17_2_1 arranged along the y-direction and improving heat transfer rate with the gas, and a plurality of 1 st flat portions 17_1_2 arranged along the y-direction. The 2 nd heat transfer promoting portions 17_2_1 and the 2 nd flat portions 17_2_2 are alternately arranged along the y direction.
In the 2 nd heat transfer promoting portion 17_2_1, 3 slits 21 are arranged in parallel in the x direction. The 2 nd flat portion 17_2_2 is a flat rectangular-shaped region between the 2 nd heat transfer promoting portions 17_2_1 of the fins 16. The length of the 2 nd flat portion 17_2_2 in the y direction is the same as the length of the 2 nd heat transfer promoting portion 17_2_1 in the y direction.
The 1 st heat transfer promoting portion 17_1_1 is arranged with the 2 nd heat transfer promoting portion 17_2_1 in the x direction, and the 1 st flat portion 17_1_2 is arranged with the 2 nd flat portion 17_2_2 in the x direction.
In the 2 nd heat transfer tube 15_2, fins 16 are provided along the y direction. The 2 nd heat transfer pipe 15_2 is provided between the 1 st header tank 12_1 and the 2 nd header tank 13_1. The fin 16 has a1 st extension 16_1 and a2 nd extension 16_2.
The 1 st extension portion 16_1 of the fin 16 has a rectangular shape, one of the long sides is attached to the 2 nd heat transfer tube 15_2 in the y direction, and the short side is disposed so as to extend upward in the x direction.
The 2 nd extension portion 16_2 of the fin 16 has a rectangular shape, one of the long sides is attached to the 2 nd heat transfer tube 15_2 in the y direction, and the short side is disposed so as to extend downstream in the x direction.
The 1 st extension 16_1 is provided on the upstream side of the gas passing through the fin 16. When viewed from the z direction, the 1 st extension portion 16_1 has a rectangular shape, and the long side thereof is provided in the 1 st heat transfer tube 15_1. The 1 st extension portion 16_1 is provided with a1 st heat transfer promoting region 17_1 that increases the heat transfer rate between the 1 st extension portion 16_1 and the gas. The 1 st heat transfer promoting region 17_1 includes a plurality of 1 st heat transfer promoting portions 17_1_1 arranged along the y-direction and improving the heat transfer rate with the gas, and a plurality of 1 st flat portions 17_1_2 arranged along the y-direction. The 1 st heat transfer promoting portions 17_1_1 and the 1 st flat portions 17_1_2 are alternately arranged along the y direction.
In the 1 st heat transfer promoting portion 17_1_1, 3 slits 21 are arranged in parallel in the x direction. The 1 st flat portion 17_1_2 is a flat rectangular-shaped region between the 1 st heat transfer promoting portions 17_1_1 of the fins 16. The length of the 1 st flat portion 17_1_2 in the y direction is the same as the length of the 1 st heat transfer promoting portion 17_1_1 in the y direction.
The 2 nd extension 16_2 is provided on the downstream side of the gas passing through the fin 16. When viewed from the z direction, the 2 nd extension portion 16_2 has a rectangular shape, and the long side thereof is provided in the 1 st heat transfer tube 15_1. The 2 nd extension portion 16_2 is provided with a2 nd heat transfer promoting region 17_2 that increases the heat transfer rate between the 2 nd extension portion 16_2 and the gas. The 2 nd heat transfer promoting region 17_2 includes a plurality of 2 nd heat transfer promoting portions 17_2_1 arranged along the y-direction and improving heat transfer rate with the gas, and a plurality of 1 st flat portions 17_1_2 arranged along the y-direction. The 2 nd heat transfer promoting portions 17_2_1 and the 2 nd flat portions 17_2_2 are alternately arranged along the y direction.
In the 2 nd heat transfer promoting portion 17_2_1, 3 slits 21 are arranged in parallel in the x direction. The 2 nd flat portion 17_2_2 is a flat rectangular-shaped region between the 2 nd heat transfer promoting portions 17_2_1 of the fins 16. The length of the 2 nd flat portion 17_2_2 in the y direction is the same as the length of the 2 nd heat transfer promoting portion 17_2_1 in the y direction.
The 1 st heat transfer promoting portion 17_1_1 is arranged with the 2 nd heat transfer promoting portion 17_2_1 in the x direction, and the 1 st flat portion 17_1_2 is arranged with the 2 nd flat portion 17_2_2 in the x direction.
The position in the y direction of the 2 nd heat transfer promoting portion 17_2_1 formed on the fin 16 provided to the 1 st heat transfer tube 15_1 is different from the position in the y direction of the 1 st heat transfer promoting portion 17_1_1 formed on the fin 16 provided to the 2 nd heat transfer tube 15_2.
Fig. 10 is a diagram showing a modification of the heat exchange member 14 of the heat exchanger 11 according to embodiment 5. In fig. 10, white arrows show the direction of the gas flow. In embodiment 5, the plurality of heat exchange members 14 shown in fig. 2 are provided at intervals in the z direction, and 3 rows are provided in the x direction. In fig. 10, the 1 st column heat exchange member 14_1, the 2 nd column heat exchange member 14_2, and the 3 rd column heat exchange member 14_3 are shown as examples thereof.
The 1 st heat transfer promoting portions 17_1_1 and 1 st flat portions 17_1_2 formed on the fins 16 provided on the 1 st heat transfer tube 15_1, the 2 nd heat transfer tube 15_2 and the 3 rd heat transfer tube 15_3 are the same as those of fig. 5.
As shown in fig. 10, the position in the 2 nd direction of the 2 nd heat transfer promoting portion 17_2_1 provided in the 1 st heat transfer tube 15_1 is different from the position in the 2 nd direction of the 1 st heat transfer promoting portion 17_1_1 provided in the 2 nd heat transfer tube 15_2. The position in the y direction of the 2 nd heat transfer promoting portion 17_2_1 provided in the 2 nd heat transfer pipe 15_2 is different from the position in the y direction of the 1 st heat transfer promoting portion 17_1_1 provided in the 3 rd heat transfer pipe 15_3.
According to embodiment 5, the 1 st heat transfer promoting portions 17_1_1 of adjacent heat transfer tubes 15 are positioned differently in the 2 nd direction. Therefore, the pressure loss distribution of the air flow in the y direction becomes uniform, and as a result of the air flow passing through the 1 st flat portion 17_1_2 and the 2 nd flat portion 17_2_2 being reduced, the heat transfer rate between the air flow and the fins 16 is improved.
Even if the air flow passes through the 1 st flat portion 17_1_2 and the 2 nd flat portion 17_2_2, the plurality of fins 16 are arranged in the x direction, which is the flow direction of the air flow, and therefore, the path of the air flow is lengthened, and the substantial heat transfer area can be enlarged.
Summary of effects
In the case where the heat transfer tube 15 is a round tube or a flat tube, the air flow does not easily flow before and after the heat transfer tube 15, and therefore, as in embodiments 1 to 5, the technical idea of providing the fins 16 with both the 1 st heat transfer promoting region 17_1 and the 2 nd heat transfer promoting region 17_2 is not originally provided. Further, the technical idea of promoting the heat transfer effect by the arrangement or combination of the 1 st heat transfer promoting portion 17_1_1 in the 1 st heat transfer promoting region 17_1 and the 2 nd heat transfer promoting portion 17_2_1 in the 2 nd heat transfer promoting region 17_2 does not exist.
In the heat exchanger 11 according to embodiments 1 to 5, the 1 st heat transfer promoting portion 17_1 is formed in the fin 16 extending toward the upwind side, and the 2 nd heat transfer promoting portion 17_2_1 is formed in the fin 16 extending toward the downwind side, so that the fin 16 has a large influence on the heat transfer efficiency.
In embodiments 1 to 5, it is described that the 1 st heat transfer promoting portion 17_1_1 and the 2 nd heat transfer promoting portion 17_2_1 can be constituted by any one or more of a cut-up portion, a slit, a louver, and a concave-convex portion. In the case where the cut-up portions, slits, or louvers are used, since the openings are provided in the fins 16, the area of the planar portions of the fins 16, that is, the area where heat exchange with the gas is performed, is reduced. Here, unlike embodiment 1 to embodiment 5, in the heat exchanger in which the heat transfer tube 15 penetrates the fins 16, the entire outer peripheral surface of the heat transfer tube is in contact with the fins, and therefore, the direction of heat conduction from the heat transfer tube 15 to the fins 16 is 360 degrees when viewed in the cross section of the heat transfer tube 15. Therefore, the influence on the reduction of the heat exchange area due to the provision of the openings in the fins 16 is limited. However, in the heat exchangers according to embodiments 1 to 5, the fins 16 are connected to the side of the heat transfer tube 15 in the y direction or the x-y plane (fig. 4) of the heat transfer tube 15, and therefore, the direction of heat conduction from the heat transfer tube 15 to the fins 16 is limited. Therefore, in embodiments 1 to 5, the effect on the reduction of the heat exchange area due to the provision of the openings in the fins 16 is large compared to the heat exchanger in which the heat transfer tubes pass through the fins. Therefore, the opening area of the fin 16 and the arrangement of the 1 st heat transfer promoting portions 17_1_1 and the 2 nd heat transfer promoting portions 17_2_1 in embodiments 1 to 5 will be described below.
Fig. 11 is a diagram showing the arrangement of the 1 st heat transfer promoting portion 17_1_1 and the 2 nd heat transfer promoting portion 17_2_1 formed on the fin 16 of the comparative example. Fig. 11 shows a1 st heat transfer tube 15_1 and a2 nd heat transfer tube 15_2 arranged at intervals in the x-direction. As shown in fig. 11, the 1 st heat transfer promoting portion 17_1_1 is arranged in the x direction of the 1 st heat transfer promoting portion 17_1_1, and the 2 nd heat transfer promoting portion 17_2_1 is arranged. Further, the 1 st flat portion 17_1_2 is arranged in the x direction of the 1 st flat portion 17_1_2, and the 2 nd flat portion 17_2_2 is arranged in the x direction.
Fig. 12 is a graph showing a relationship between the gap area ratio and the air-side heat transfer performance. The "gap area ratio" is the gap area/the area of the fin 16. The "air-side heat transfer performance" is the air-side heat transfer area x air-side heat conductivity of the fins 16.
In fig. 12, g_1 shows the characteristics of the gap area ratio and the air-side heat transfer performance of the heat exchanger 11 shown in fig. 11. g2 shows the characteristics of the gap area ratio and the air side heat transfer performance of the heat exchanger 11 shown in fig. 9. g3 shows characteristics of a gap area ratio and air-side heat transfer performance in the case where the heat exchanger 11 shown in fig. 5 is provided with 2 rows in the x direction. g4 shows characteristics of a gap area ratio and air-side heat transfer performance in the case where the heat exchanger 11 shown in fig. 8 is provided with 2 rows in the x direction.
As shown in fig. 12, if the gap area ratio is the same, the air-side heat transfer performance of the fin 16 shown in fig. 8 is the highest. Next, the fins 16 shown in fig. 5 and the fins 16 shown in fig. 9 have high air-side heat transfer performance, and the fins 16 shown in fig. 5, 8 and 9 have higher air-side heat transfer performance than the fins 16 shown in fig. 11 as a comparative example. The other fins 16 according to embodiments 1 to 5 have higher air-side heat transfer performance than the fins 16 shown in fig. 11 as comparative examples.
In the case of the structure of the heat exchanger 11 of fig. 9, the air-side heat transfer performance is higher in the case of the gap area ratio of 7.5% than in the case of 15%, as shown in g_2 of fig. 12. Therefore, in the case of adopting the structure of the heat exchanger 11 of fig. 9, the gap area ratio is preferably set to 7.5%. Further, as shown in fig. 12, in g_1, a peak in air-side heat transfer performance occurs at a gap area ratio of 7.5%. In any of the patterns according to embodiments 1 to 5, the slit area ratio is preferably 5% to 10%. The slit area ratio is defined in this way to suppress a decrease in the heat transfer easiness, that is, the heat conductivity in the fins 16 and to improve the heat transfer ratio of the 1 st heat transfer promoting portion 17_1_1 and the 2nd heat transfer promoting portion 17_2_1.
In embodiments 1 to 5, the shape of the 1 st heat transfer promoting portion 17_1_1 and the 2 nd heat transfer promoting portion 17_2_1 may be different. For example, the 1 st heat transfer promoting portion 17_1_1 may be formed as the slit 21, and the 2 nd heat transfer promoting portion 17_2_1 may be formed as the concave-convex shape. In order to avoid frosting, the number of slits 21 of the 1 st heat transfer promoting portion 17_1_1 may be smaller than the number of slits 21 of the 2 nd heat transfer promoting portion 17_2_1.
In addition, the 1 st heat transfer promoting portion 17_1_1 may have a different shape. For example, the 1 st heat transfer promoting portion 17_1_1 may have a slit 21 and a louver. Similarly, the shape of the 2 nd heat transfer promoting portion 17_2_1 may be different. For example, the 2 nd heat transfer promoting portion 17_2_1 may have the slit 21 and the concave-convex shape.
Embodiments 1 to 5 are presented as examples, and are not intended to limit the claims. The embodiments may be implemented in other various forms, and various omissions, substitutions, and changes may be made without departing from the spirit of the embodiments. These embodiments and modifications thereof are included in the scope and gist of the embodiments.
Description of the reference numerals
1: An air conditioning device; 2: a compressor; 3: an outdoor heat exchanger; 4: an expansion valve; 5: an indoor heat exchanger; 6: a four-way valve; 7: an outdoor fan; 8: an indoor fan; 11: a heat exchanger; 12. 12_1, 12_2: a 1 st header tank; 13. 13_1, 13_2: a 2 nd header tank; 14. 14_1, 14_2, 14_3: a heat exchange member; 15: a heat transfer tube; 15_1: a 1 st heat transfer pipe; 15_2: a 2 nd heat transfer pipe; 15_3: a 3 rd heat transfer pipe; 16: a fin; 16_1: a 1 st extension; 16_2: a 2 nd extension; 16_3: a main body portion; 17_1: a 1 st heat transfer promoting region; 17_1_1: a 1 st heat transfer promoting unit; 17_1_2: 1 st flat portion; 17_2: a 2 nd heat transfer promoting region; 17_2_1: a 2 nd heat transfer promoting portion; 17_2_2: a 2 nd flat portion; 21: a cutting-up part; 22: a concave-convex portion; g_1: the characteristics of the gap area ratio and the air-side heat transfer performance of the heat exchanger 11 shown in fig. 11; g_2: the characteristics of the gap area ratio and the air-side heat transfer performance of the heat exchanger 11 shown in fig. 9; g_3, g_4: the heat exchanger 11 shown in fig. 4 has characteristics of a gap area ratio and air side heat transfer performance in the case where 2 rows are provided in the x direction.
Claims (9)
1. A heat exchanger, wherein the heat exchanger has:
A heat transfer pipe extending in a 2 nd direction intersecting the 1 st direction of the gas flow; and
Fins provided on the heat transfer pipe and having surfaces along the 1 st and 2 nd directions,
The fin has:
A1 st extension portion provided on an upstream side of the heat transfer pipe with respect to the gas in the 1 st direction, the extension portion having a1 st heat transfer promoting region for improving a heat transfer rate; and
And a2 nd extension portion provided downstream of the heat transfer pipe with respect to the gas in the 1 st direction, the extension portion having a2 nd heat transfer promoting region for improving a heat transfer rate.
2. The heat exchanger of claim 1, wherein,
The 1 st heat transfer promoting region has:
a plurality of 1 st heat transfer promoting units arranged along the 2 nd direction to increase the heat transfer rate; and
A1 st flat portion arranged between the adjacent 1 st heat transfer promoting portions in the 2 nd direction,
The 2 nd heat transfer promoting region has:
A plurality of 2 nd heat transfer promoting units arranged along the 2 nd direction to increase the heat transfer rate; and
And a2 nd flat portion disposed between the 2 nd heat transfer promoting portions adjacent to each other in the 2 nd direction.
3. The heat exchanger of claim 2, wherein,
The 1 st heat transfer promoting portions and the 1 st flat portions are alternately arranged along the 2 nd direction,
The 2 nd heat transfer promoting portions and the 2 nd flat portions are alternately arranged along the 2 nd direction,
The 2 nd flat portion is disposed in the 2 nd heat transfer promoting region juxtaposed with the 1 st heat transfer promoting portion in the 1 st direction, and the 2 nd heat transfer promoting portion is disposed in the 2 nd heat transfer promoting region juxtaposed with the 1 st flat portion in the 1 st direction.
4. A heat exchanger according to claim 2 or 3 wherein,
The heat transfer pipe has a plurality of heat transfer pipes arranged at predetermined intervals in a3 rd direction intersecting the 1 st direction and the 2 nd direction.
5. A heat exchanger according to any one of claims 2 to 4 wherein,
The 1 st heat transfer promoting portion, the 2 nd heat transfer promoting portion, the 1 st flat portion, and the 2 nd flat portion have the same length in the 2 nd direction,
The position of the 1 st heat transfer promoting portion in the 2 nd direction is the same as the position of the 2 nd flat portion in the 2 nd heat transfer promoting region in the 2 nd direction,
The position of the 1 st flat portion in the 2 nd direction is the same as the position of the 2 nd heat transfer promoting portion in the 2 nd heat transfer promoting region in the 2 nd direction.
6. The heat exchanger of claim 1, wherein,
The 1 st heat transfer promoting region has a plurality of 1 st heat transfer promoting portions arranged along the 2 nd direction and improving heat transfer rate,
The 2 nd heat transfer promoting region has a plurality of 2 nd heat transfer promoting portions arranged along the 2 nd direction and improving heat transfer rate,
Any one of a cut-up portion, a slit, a louver, and a concave-convex portion is formed in the 1 st heat transfer promoting portion,
Any one of a cut-up portion, a slit, a louver, and a concave-convex portion is formed in the 2 nd heat transfer promoting portion,
The sum of the number of any of the cut-up portions, slits, louvers, and concavities and convexities formed in the 1 st heat transfer promoting portion in the 1 st direction and the number of any of the cut-up portions, slits, louvers, and concavities and convexities formed in the 2 nd heat transfer promoting portion in the 1 st direction is fixed.
7. A heat exchanger according to any one of claims 2 to 5 wherein,
The 1 st heat transfer promoting part is any one of a cut-up part, a slit, a shutter and a concave-convex part,
The 2 nd heat transfer promoting portion is any one of a cut-up portion, a slit, a louver, and a concave-convex portion.
8. The heat exchanger of claim 6, wherein,
A1 st pattern of any one of the slit, the louver, and the concave-convex portion is formed in the plurality of 1 st heat transfer promoting portions,
A2 nd pattern of any one of the slit, the louver, and the concave-convex portion is formed in the plurality of 2 nd heat transfer promoting portions,
The 1 st pattern and the 2 nd pattern are staggered in the 2 nd direction.
9. A heat exchanger according to any one of claims 2 to 8 wherein,
The heat exchanger has groups 1 and 2 including the heat transfer pipe and the fins respectively,
The heat transfer tubes of the 2 nd group are disposed at intervals in the 1 st direction with respect to the heat transfer tubes of the 1 st group,
The position of the 2 nd heat transfer promoting portion formed on the fin of the 1 st group in the 2 nd direction is different from the position of the 1 st heat transfer promoting portion formed on the fin of the 2 nd group in the 2 nd direction.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2021/044701 WO2023105566A1 (en) | 2021-12-06 | 2021-12-06 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN118339417A true CN118339417A (en) | 2024-07-12 |
Family
ID=86729773
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202180104564.8A Pending CN118339417A (en) | 2021-12-06 | 2021-12-06 | Heat exchanger |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPWO2023105566A1 (en) |
| CN (1) | CN118339417A (en) |
| WO (1) | WO2023105566A1 (en) |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6237692A (en) * | 1985-08-12 | 1987-02-18 | Hitachi Ltd | Heat exchanger |
| JP3863034B2 (en) * | 2002-02-22 | 2006-12-27 | 東芝キヤリア株式会社 | Heat exchanger |
| JP7044786B2 (en) | 2017-08-03 | 2022-03-30 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle equipment |
| JP6980117B2 (en) * | 2018-08-27 | 2021-12-15 | 三菱電機株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
-
2021
- 2021-12-06 JP JP2023565674A patent/JPWO2023105566A1/ja not_active Withdrawn
- 2021-12-06 CN CN202180104564.8A patent/CN118339417A/en active Pending
- 2021-12-06 WO PCT/JP2021/044701 patent/WO2023105566A1/en active Application Filing
Also Published As
| Publication number | Publication date |
|---|---|
| WO2023105566A1 (en) | 2023-06-15 |
| JPWO2023105566A1 (en) | 2023-06-15 |
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