CN114072627B - Heat transfer tube and heat exchanger using the same - Google Patents
Heat transfer tube and heat exchanger using the same Download PDFInfo
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- CN114072627B CN114072627B CN201980097777.5A CN201980097777A CN114072627B CN 114072627 B CN114072627 B CN 114072627B CN 201980097777 A CN201980097777 A CN 201980097777A CN 114072627 B CN114072627 B CN 114072627B
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- heat transfer
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- wall
- transfer tube
- flat
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- 238000012546 transfer Methods 0.000 title claims abstract description 197
- 239000000463 material Substances 0.000 claims abstract description 35
- 238000005452 bending Methods 0.000 claims abstract description 24
- 239000012530 fluid Substances 0.000 claims description 33
- 230000001737 promoting effect Effects 0.000 claims description 9
- 230000005484 gravity Effects 0.000 claims description 2
- 229910000679 solder Inorganic materials 0.000 claims description 2
- 238000010276 construction Methods 0.000 claims 1
- 238000012986 modification Methods 0.000 description 9
- 230000004048 modification Effects 0.000 description 9
- 238000005219 brazing Methods 0.000 description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 7
- 238000009833 condensation Methods 0.000 description 6
- 230000005494 condensation Effects 0.000 description 6
- 238000005192 partition Methods 0.000 description 6
- 239000003507 refrigerant Substances 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 4
- 229910052782 aluminium Inorganic materials 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 3
- 239000011248 coating agent Substances 0.000 description 3
- 238000000576 coating method Methods 0.000 description 3
- 239000000945 filler Substances 0.000 description 3
- 238000005304 joining Methods 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 239000007769 metal material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000010257 thawing Methods 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- 239000004215 Carbon black (E152) Substances 0.000 description 1
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 239000012267 brine Substances 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- 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
- 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
- F28D1/03—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 plate-like or laminated conduits
- F28D1/0391—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 plate-like or laminated conduits a single plate being bent to form one or more conduits
-
- 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
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 transfer tube is provided with: a flat body portion having a plurality of flow paths formed by bending one sheet of material a plurality of times; and an extension portion formed by extending at least one end portion of the plate material in a flat long axis direction indicating a long axis direction in a cross section of the body portion, the extension portion having a length longer than a flat short axis length.
Description
Technical Field
The present invention relates to a heat transfer pipe through which a heat exchange fluid flows, and a heat exchanger using the heat transfer pipe.
Background
Conventionally, as a heat transfer tube used for a heat exchanger, a flat heat transfer tube has been known. For example, patent document 1 discloses a flat heat transfer tube formed by bending a single plate material a plurality of times. The heat transfer tube of patent document 1 includes: a flat plate-shaped base portion; two bending portions which are respectively bent from both end portions of the base portion toward a central portion of the base portion; and two partition portions respectively bent from the ends of the two bending portions on the central portion side of the base portion toward the base portion. The base-portion-side ends of the two partition portions of the heat transfer tube are further bent toward the base portion ends, and the overlapping portions overlapping the base portions are joined by brazing filler metal.
Prior art documents
Patent literature
Patent document 1: japanese patent laid-open publication No. 2018-204919
Disclosure of Invention
Problems to be solved by the invention
Recently, however, in a refrigeration cycle apparatus using an HFC (hydrofluorocarbon) refrigerant, it is demanded to reduce the refrigerant charge amount due to the influence on the global environment. In order to reduce the refrigerant charge amount, it is necessary to reduce the internal volume of the heat transfer tube in the heat exchanger constituting the refrigeration cycle apparatus. In the flat heat transfer tube disclosed in patent document 1, which is formed by bending a single plate, it is necessary to make the thickness of the plate thicker or to make the flat short-axis length or the flat long-axis length of the heat transfer tube shorter in order to reduce the internal volume.
However, in the case of making the thickness of the plate thicker, the material cost increases, and the weight of the heat transfer pipe increases. In addition, when the length of the flat minor axis or the length of the flat major axis is shortened, the heat transfer area outside the heat transfer tube becomes small, and therefore, the heat exchange performance of the heat exchanger is degraded. Further, there is a possibility that the compressor power increases due to the decrease of the heat exchange performance.
The present invention has been made in view of the problems of the conventional techniques, and an object thereof is to provide a heat transfer tube having a flat shape and formed by bending a plate material, which can suppress a decrease in heat exchange performance, and a heat exchanger using the heat transfer tube.
Means for solving the problems
The heat transfer tube of the present invention comprises: a flat body portion having a plurality of flow paths formed by bending one sheet of material a plurality of times; and an extension portion formed by extending at least one end portion of the plate material in a flat major axis direction indicating a major axis direction in a cross section of the body portion, the extension portion having a length longer than a flat minor axis length.
The heat exchanger of the present invention further includes a plurality of heat transfer tubes of the present invention, the plurality of heat transfer tubes being arranged in parallel in a direction perpendicular to a flow direction of the first heat exchange fluid flowing through the plurality of flow paths and a flow direction of the second heat exchange fluid flowing along the outer surface of the main body.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, the body portion and the extension portion are formed by bending one plate material, and the length of the extension portion is formed to be longer than the length of the flat minor axis, so that in the flat heat transfer tube formed by bending the plate material, a decrease in heat exchange performance can be suppressed.
Drawings
Fig. 1 is a perspective view showing an example of the structure of a heat transfer tube according to embodiment 1.
Fig. 2 is a schematic cross-sectional view of the heat transfer pipe when one example of the heat transfer pipe of embodiment 1 is viewed from the third direction.
Fig. 3 is a side view of the heat transfer pipe of the first modification of the heat transfer pipe of embodiment 1, as viewed from the third direction.
Fig. 4 is a side view of the heat transfer pipe of the second modification of the heat transfer pipe of embodiment 1 as viewed from the third direction.
Fig. 5 is a schematic cross-sectional view of the heat transfer pipe when one example of the heat transfer pipe of embodiment 2 is viewed from the third direction.
Fig. 6 is a schematic cross-sectional view of the heat transfer pipe when one example of the heat transfer pipe of embodiment 3 is viewed from the third direction.
Fig. 7 is a schematic cross-sectional view of the heat transfer pipe when one example of the heat transfer pipe of embodiment 4 is viewed from the third direction.
Fig. 8 is a schematic cross-sectional view of the heat transfer pipe of the example of the heat transfer pipe of embodiment 5, as viewed from the third direction.
Fig. 9 is a schematic cross-sectional view of a heat transfer tube in the case where one example of the heat transfer tube of embodiment 6 is viewed from the third direction.
Fig. 10 is a perspective view showing an example of the structure of the heat transfer tube according to embodiment 7.
Fig. 11 is a schematic cross-sectional view showing an example of the structure of the heat exchanger according to embodiment 8.
Fig. 12 is a schematic cross-sectional view showing another example of the structure of the heat exchanger according to embodiment 8.
Fig. 13 is a schematic diagram showing an example of the structure of the heat exchanger according to embodiment 9.
Detailed Description
Embodiments of the present invention will be described below with reference to the drawings. The present invention is not limited to the following embodiments, and various modifications can be made without departing from the gist of the present invention. In addition, the present invention includes all combinations of combinable ones of the structures shown in the following embodiments. The heat transfer pipe and the heat exchanger shown in the drawings below represent examples of devices to which the heat transfer pipe and the heat exchanger of the present invention are applied, and the application device of the present invention is not limited to the heat transfer pipe and the heat exchanger shown in the drawings. In the drawings, the same or corresponding portions are denoted by the same reference numerals, and are common throughout the specification. In the drawings, the relative dimensional relationship, shape, and the like of the constituent members may be different from actual ones.
Embodiment 1
The heat transfer tube of embodiment 1 will be described. The heat transfer tube according to embodiment 1 is used, for example, as a heat exchanger constituting a refrigeration cycle apparatus.
[ Structure of Heat transfer tube ]
Fig. 1 is a perspective view showing an example of the structure of a heat transfer tube according to embodiment 1. As shown in fig. 1, the heat transfer tube 1 includes a main body portion 1A and an extension portion 1B. The body portion 1A and the extension portion 1B of the heat transfer tube 1 are formed by bending one sheet of a metal material having high heat conductivity such as aluminum, copper, or brass a plurality of times.
(Main body 1A)
The body portion 1A is formed in a flat shape having a substantially oval cross section. A plurality of flow passages are formed in the main body 1A along the longitudinal direction of the heat transfer tube 1, and the first heat exchange fluid flows through these flow passages. The first heat exchange fluid is, for example, water, brine, HFC-based refrigerant, and HC (hydrocarbon) -based refrigerant.
Here, in embodiment 1, a flat long axis direction indicating a long axis direction in a cross-sectional shape cut by a plane perpendicular to the flow path of the main body 1A is defined as a first direction. In addition, a flat minor axis direction indicating a minor axis direction in a cross-sectional shape orthogonal to the first direction and cut by a plane perpendicular to the flow path of the main body 1A is defined as a second direction. The direction orthogonal to the first direction and the second direction and through which the first heat exchange fluid flows is defined as a third direction.
The second heat exchange fluid flows on the outer surface of the body portion 1A in a direction parallel to the first direction or the third direction. The second heat exchange fluid is, for example, air. In fig. 1, the flow direction of the first heat exchange fluid and the second heat exchange fluid is indicated by open arrows.
(extension 1B)
The extension portion 1B is formed to extend from the body portion 1A in the first direction. The extension 1B is formed by an end of one sheet of material forming the body 1A and the extension 1B.
Fig. 2 is a schematic cross-sectional view of the heat transfer tube of the example of the heat transfer tube of embodiment 1, as viewed from the third direction. As shown in fig. 2, the main body 1A is composed of a tube outer wall 10 which is an outer surface of the heat transfer tube 1 formed by bending one sheet of material a plurality of times, and a tube inner wall 11 which is a wall portion other than the tube outer wall 10.
The tube outer wall 10 is constituted by a portion of the body portion 1A that is in contact with the second heat exchange fluid and a portion adjacent to the portion. The pipe inner wall 11 is formed by a portion of the main body 1A other than the pipe outer wall 10, and includes 2 or more overlapping portions 11A and at least 1 partition portion 11b.
The overlapping portion 11a of the pipe inner wall 11 is a portion overlapping the pipe outer wall 10, and is joined to the pipe outer wall 10 by brazing, for example. The partition 11b is a portion that is formed by bending a plate material to divide the interior of the main body 1A.
In this way, the internal space of the body portion 1A surrounded by the overlapping portion 11A and the partition portion 11b of the tube outer wall 10 and the tube inner wall 11 becomes a plurality of flow paths through which the 1 st heat exchange fluid flows. Hereinafter, the length of the body portion 1A in the flat major axis direction (first direction) when the heat transfer tube 1 is viewed from the third direction is defined as a flat major axis length DA, and the length in the flat minor axis direction (second direction) is defined as a flat minor axis length DB.
The extension portion 1B is formed by extending at least one end portion of the plate material from the body portion 1A in the flat long axis direction as the first direction. In addition, the extension portion 1B is formed longer than the flat minor axis length DB of the body portion 1A. This is to improve the heat transfer performance of the heat exchanger in the case where the heat transfer pipe 1 is used for the heat exchanger. The heat transfer performance of the heat exchanger will be described later.
In the example shown in fig. 2, two extension portions 1B are formed by extending both ends of the plate material in the opposite flat long axis directions, but the present invention is not limited to this example. For example, the heat transfer pipe 1 may be formed with only one extension portion 1B.
(first modification)
Fig. 3 is a side view of the heat transfer pipe according to the first modification of the heat transfer pipe of embodiment 1, as viewed from the third direction. In the heat transfer tube 1 shown in fig. 3, one extension portion 1B is bent so as to overlap the other extension portion 1B. In this way, in the heat transfer tube 1 of embodiment 1, only one extension portion 1B may be formed. In this way, the extension portion 1B and a part of the tube outer wall 10 of the body portion 1A have a double structure, and the thickness of the extension portion 1B and the tube outer wall 10 can be increased, so that the pressure resistance and durability of the heat transfer tube 1 can be improved.
(second modification)
Fig. 4 is a side view of the heat transfer pipe according to the second modification of the heat transfer pipe of embodiment 1, as viewed from the third direction. In the heat transfer tube 1 shown in fig. 4, the heat transfer tube 1 is formed such that one end of the plate material serves as the tube inner wall 11. Thereby, the heat transfer pipe 1 forms only one extension portion 1B. Therefore, the extension portion 1B of the heat transfer tube 1 and a part of the tube outer wall 10 of the main body portion 1A of the second modification are not double-structured. Therefore, compared to the heat transfer tube 1 of modification 1, the amount of material used and the amount of solder used for joining the portions having the double structure can be reduced, and the manufacturing cost of the heat transfer tube 1 can be suppressed.
(Heat transfer Property of Heat exchanger)
Next, the heat transfer performance of the heat exchanger using the heat transfer tube 1 of embodiment 1 will be described. The heat transfer performance of the heat exchanger can generally be determined using the total heat transfer coefficient AoK. The total heat transfer coefficient AoK is calculated according to equation (1). In the formula (1), ao represents the heat transfer area outside the tube, K represents the heat transfer coefficient, ap represents the heat transfer tube surface area, η represents the fin efficiency, A F Represents the surface area of the fin, αo represents the heat conductivity (including contact thermal resistance) outside the tube, ai represents the heat transfer area inside the tube, and αi represents the heat conductivity in the tube.
[ mathematics 1]
As can be seen from the formula (1), by increasing the heat transfer tube surface area Ap and the fin surface area A F The heat transfer performance of the heat exchanger can be improved. That is, since the heat transfer tube 1 of embodiment 1 is provided with the extension portion 1B integrally formed with the main body portion 1A, even when the tube shape of the main body portion 1A is the same as that of the conventional one, the heat transfer area Ao outside the tube can be made larger than that of the conventional one. In addition, even when the volume inside the heat transfer tube 1 is made smaller than before in accordance with environmental restrictions or the like, by making the length of the extension portion 1B longer, the tube internal volume can be reduced, and the heat transfer area Ao outside the tube can be ensured as much as before.
As described above, in the heat transfer tube 1 of embodiment 1, the body portion 1A through which the first heat exchange fluid flows is formed by bending one plate material a plurality of times, and the extension portion 1B is formed by extending at least one end portion of the plate material in the flat long axis direction. In this way, since the extension portion 1B is formed in the heat transfer tube 1, even when the tube shape of the body portion 1A is the same as the conventional one, the heat transfer area Ao outside the tube can be made larger than the conventional one. Therefore, in the case where the heat transfer pipe 1 is used for a heat exchanger, the heat transfer performance of the heat exchanger can be improved.
In addition, the extension portion 1B of the heat transfer tube 1 is formed longer than the flat minor axis length DB. In this way, in the bending process at the time of manufacturing the heat transfer tube 1, the extension portion 1B is used as a grip portion of the manufacturing apparatus, and therefore the manufacturability of the heat transfer tube 1 can be improved.
As a plate material for forming the heat transfer pipe 1, a coating material may be used in which aluminum or the like is used as a base material and both surfaces of the base material are coated with a brazing filler metal. By using the coating material as the plate material, a step of coating the brazing filler metal on the surface of the plate material is not required in manufacturing the heat transfer tube 1, and therefore, the manufacturability of the heat transfer tube 1 can be improved.
Embodiment 2
Next, embodiment 2 will be described. The present embodiment 2 is different from embodiment 1 in that the tube outer wall 10 in the flat short axis direction is formed in a double structure. In embodiment 2, the same reference numerals are given to the portions common to embodiment 1, and detailed description thereof is omitted.
Fig. 5 is a schematic cross-sectional view of the heat transfer tube of the example of the heat transfer tube of embodiment 2, as viewed from the third direction. As shown in fig. 5, the heat transfer tube 1 of embodiment 2 is formed with an outer wall overlapping portion 10a where the tube outer wall 10 in the flat short axis direction has a double structure.
The outer wall overlapping portion 10a is formed by bending the tube outer wall 10 in the flat minor axis direction at the boundary portion between the body portion 1A and the extension portion 1B of embodiment 1. The outer wall overlapping portions 10a are joined by brazing, for example. As a result, the tube outer wall 10 in the flat short axis direction becomes stronger, and the pressure resistance and durability of the heat transfer tube 1 can be improved.
Further, the longer the outer wall overlapping portion 10a, the larger the adhesion area of the material forming the pipe outer wall 10, and the higher the joining strength. Therefore, the length of the outer wall overlapping portion 10a is preferably 1/2 or more of the flat minor axis length DB, for example.
As described above, when the heat transfer tube 1 according to embodiment 2 is used in a heat exchanger, the heat transfer performance of the heat exchanger can be improved as in embodiment 1. In the heat transfer tube 1 according to embodiment 2, an outer wall overlapping portion 10a having a double structure is formed in the tube outer wall 10 provided in the flat minor axis direction. The length of the outer wall overlapping portion 10a is preferably 1/2 or more of the flat minor axis length DB. In this way, the tube outer wall 10 in the flat short axis direction becomes stronger, and the pressure resistance and durability of the heat transfer tube 1 can be improved.
Embodiment 3
Next, embodiment 3 will be described. Embodiment 3 differs from embodiments 1 and 2 in that the end portion of the main body portion 1A in the flat major axis direction is formed in an R shape and the extension portion 1B is located on the substantially central axis in the flat minor axis direction. In embodiment 3, the same reference numerals are given to the portions common to embodiments 1 and 2, and detailed description thereof is omitted.
Fig. 6 is a schematic cross-sectional view of the heat transfer tube of the example of the heat transfer tube of embodiment 3, as viewed from the third direction. As shown in fig. 6, in the heat transfer tube 1 of embodiment 3, the end portion of the body portion 1A in the flat long axis direction is formed in an R shape. In addition, the extension portion 1B is formed on the substantially central axis of the flat minor axis length DB.
The tube outer wall 10 of the main body 1A is formed by bending a plate material so that an end in the flat longitudinal direction is R-shaped. The extension portion 1B is formed by bending a plate material along the R-shape of the tube outer wall 10 of the main body portion 1A and bending again in the vicinity of the central axis of the flat minor axis length DB.
In the case where the body portion 1A and the extension portion 1B are formed in this way, the second heat exchange fluid first flows along the extension portion 1B. Then, the second heat exchange fluid collides with the body portion 1A along the R shape of the body portion 1A. At this time, the flow resistance due to the collision of the second heat exchange fluid with the body portion 1A is reduced as compared with the body portion 1A in which the R shape is not formed.
As described above, when the heat transfer pipe 1 according to embodiment 3 is used in a heat exchanger, the heat transfer performance of the heat exchanger can be improved as in embodiments 1 and 2. In the heat transfer tube 1 according to embodiment 3, the end portion of the body portion 1A in the flat major axis direction is formed in an R shape, and the extension portion 1B is formed on the central axis of the flat minor axis length DB. Thereby, the flow resistance due to the collision of the second heat exchange fluid flowing through the heat transfer tube 1 with the body portion 1A is reduced. Therefore, the driving force of the blower or the like that supplies the second heat exchange fluid can be reduced.
Embodiment 4
Next, embodiment 4 will be described. Embodiment 4 differs from embodiments 1 to 3 in that a part of the tube outer wall 10 of the body portion 1A is curved toward the central axis in the flat minor axis direction. In embodiment 4, the same reference numerals are given to the portions common to embodiments 1 to 3, and detailed description thereof is omitted.
Fig. 7 is a schematic cross-sectional view of a heat transfer tube in the case where one example of the heat transfer tube of embodiment 4 is viewed from the third direction. As shown in fig. 7, in the heat transfer tube 1 of embodiment 4, a part of the tube outer wall 10 of the body portion 1A is formed to be curved toward the central axis of the flat minor axis length DB. At this time, the curved pipe outer wall 10 is curved in contact with the pipe inner wall 11.
As described above, when the heat transfer tube 1 according to embodiment 4 is used in a heat exchanger, the heat transfer performance of the heat exchanger can be improved as in embodiments 1 to 3. In the heat transfer tube 1 according to embodiment 4, the volume of the heat transfer tube 1, which is a flow path through which the first heat exchange fluid flows, is reduced by bending a part of the tube outer wall 10 in the central axis direction of the flat minor axis length DB, as compared with the case where the tube outer wall 10 is not bent. Therefore, the filling amount of the first heat exchanger fluid can be reduced.
On the other hand, by forming a part of the tube outer wall 10 to be curved, the heat transfer area Ao of the heat transfer tube 1 can be increased, and therefore, the heat exchange performance in the case where the heat transfer tube 1 is used for a heat exchanger can be improved. In addition, since a portion of the pipe outer wall 10 is bent so as to contact the pipe inner wall 11, the contact area between the pipe outer wall 10 and the pipe inner wall 11 increases, and therefore, the pressure resistance and durability can be improved.
Embodiment 5
Next, embodiment 5 will be described. Embodiment 5 differs from embodiments 1 to 4 in that all the pipe outer walls 10 of the main body 1A have a structure of two or more. In embodiment 5, the same reference numerals are given to the portions common to embodiments 1 to 4, and detailed description thereof is omitted.
Fig. 8 is a schematic cross-sectional view of a heat transfer tube in the case where one example of the heat transfer tube of embodiment 5 is viewed from the third direction. As shown in fig. 8, in the heat transfer tube 1 of embodiment 5, the tube outer wall 10 of the main body 1A is formed by bending 2 or more plates so as to overlap. The outer wall 10 of the pipe is joined at a position where two or more plates overlap, for example, by brazing. Thereby, all the tube outer walls 10 are formed in a double or more structure.
As described above, when the heat transfer tube 1 according to embodiment 5 is used in a heat exchanger, the heat transfer performance of the heat exchanger can be improved as in embodiments 1 to 4. In the heat transfer tube 1 according to embodiment 5, all of the tube outer walls 10 have a double or more structure. Therefore, the pressure resistance and durability can be improved as compared with embodiments 1 to 4.
Embodiment 6
Next, embodiment 6 will be described. Embodiment 6 differs from embodiments 1 to 5 in that the tube outer wall 10 and the tube inner wall 11 of the body portion 1A are formed to be point-symmetrical at the intersection point of the central axes of the flat major axis length DA and the flat minor axis length DB, respectively. In embodiment 6, the same reference numerals are given to the portions common to embodiments 1 to 5, and detailed description thereof is omitted.
Fig. 9 is a schematic cross-sectional view of a heat transfer tube in the case where one example of the heat transfer tube of embodiment 6 is viewed from the third direction. As shown in fig. 9, the pipe outer wall 10 and the pipe inner wall 11 of the main body 1A of embodiment 6 are formed by bending a plate material so as to be point-symmetrical at the intersection point of the central axes of the flat major axis length DA and the flat minor axis length DB.
As described above, when the heat transfer tube 1 according to embodiment 6 is used in a heat exchanger, the heat transfer performance of the heat exchanger can be improved as in embodiments 1 to 5. In the heat transfer tube 1 according to embodiment 6, the tube outer wall 10 and the tube inner wall 11 are formed to be point-symmetrical at the intersection points of the central axes of the flat major axis length DA and the flat minor axis length DB. Thus, even if the heat transfer tube 1 is rotated 180 ° about the axis in the third direction passing through the intersection point of the central axes of the flat major axis length DA and the flat minor axis length DB, the shape of the heat transfer tube 1 before and after rotation is the same. Therefore, when the heat exchanger is manufactured by arranging the plurality of heat transfer pipes 1, the plurality of heat transfer pipes 1 can be arranged regardless of the orientation of the heat transfer pipes 1. This can improve the manufacturability of the heat exchanger.
Embodiment 7
Next, embodiment 7 will be described. Embodiment 7 is different from embodiments 1 to 6 in that heat transfer promotion processing is performed on the extension portion 1B. In embodiment 7, the same reference numerals are given to the portions common to embodiments 1 to 6, and detailed description thereof is omitted.
Fig. 10 is a perspective view showing an example of the structure of the heat transfer tube according to embodiment 7. As shown in fig. 10, the heat transfer tube 1 includes a main body portion 1A and an extension portion 1B, as in embodiments 1 to 6. In embodiment 7, the extension portion 1B is provided with a heat transfer promoting portion 12 that promotes heat transfer of the second heat exchange fluid, such as a cut-out portion or a concave-convex portion.
The heat transfer promoting portion 12 is formed by press working the region of the extension portion 1B in the plate material. In this example, the heat transfer promoting portion 12 is provided at least on the outer side of the extension portion 1B, but the present invention is not limited thereto, and may be provided on the inner side, for example.
As described above, in the heat transfer pipe 1 according to embodiment 7, by providing the heat transfer promoting portion 12 in the extension portion 1B, when the second heat exchange fluid flows through the extension portion 1B, the second heat exchange fluid collides with the heat transfer promoting portion 12, thereby forming a vortex of fluid. In this way, since the heat transfer pipe 1 has an improved heat transfer rate outside the pipe, the heat exchange performance of the heat exchanger can be further improved when the heat transfer pipe 1 is used in a heat exchanger.
Embodiment 8
Next, embodiment 8 will be described. Embodiment 8 will explain a case where the heat transfer tube 1 described in embodiments 1 to 7 is applied to a heat exchanger. In embodiment 8, the same reference numerals are given to the portions common to embodiments 1 to 7, and detailed description thereof is omitted.
Fig. 11 is a schematic cross-sectional view showing an example of the structure of the heat exchanger according to embodiment 8. Fig. 11 shows an example of a cross section of the heat exchanger 20A cut with a plane formed by the first direction and the second direction when viewed from the third direction. As shown in fig. 11, the heat exchanger 20A is a fin-tube heat exchanger. The heat exchanger 20A is configured by arranging a plurality of heat transfer tubes 1 described in embodiments 1 to 7, and joining fins 21 between each heat transfer tube 1 and the adjacent heat transfer tube 1. Here, the heat exchanger 20A in the case where the heat transfer pipe 1 of embodiment 3 is applied is shown.
The plurality of heat transfer pipes 1 are arranged in such a manner as to extend along the third direction. In addition, the plurality of heat transfer pipes 1 are arranged in parallel along the second direction. In other words, the plurality of heat transfer pipes 1 are arranged side by side in a direction perpendicular to both the flow direction of the first heat exchange fluid and the flow direction of the second heat exchange fluid. Headers, not shown, are connected to both ends of the heat transfer tube 1 in the third direction.
The plurality of fins 21 are, for example, corrugated fins, and are disposed between adjacent heat transfer tubes 1. Each of the plurality of fins 21 is formed of a plate-like member made of a metal material having high heat conductivity, such as aluminum.
The fins 21 are formed by bending plate-like members into a shape in which planar portions and curved portions, not shown, are alternately arranged. The plurality of planar portions are arranged substantially in parallel with a predetermined interval. The curved surface portions of the plurality of fins 21 are connected to the tube outer wall 10 of the heat transfer tube 1 by brazing, welding, or the like. The planar portions of the plurality of fins 21 are provided with a process for promoting heat transfer, such as slits, cut-out, or projections and depressions.
Fig. 12 is a schematic cross-sectional view showing another example of the structure of the heat exchanger according to embodiment 8. The example of fig. 12 shows a cross section of the heat exchanger 20B cut with a plane formed by the first direction and the second direction as viewed from the third direction, similarly to fig. 11. Here, an example of the heat exchanger 20B to which the heat transfer tube 1 of embodiment 4 is applied is shown.
In the heat transfer tube 1 of embodiment 4, a part of the tube outer wall 10 is bent toward the central axis in the flat minor axis direction. Therefore, in the heat exchanger 20B, gaps 22 are formed between the heat transfer tubes 1 and the fins 21. The gap 22 functions as a water guide path for discharging dew condensation water generated when dew condensation is generated on the surface of the heat exchanger 20B.
As described above, the heat exchangers 20A and 20B according to embodiment 8 include the plurality of heat transfer tubes 1 described in embodiments 1 to 7, and the fins 21 are provided between the adjacent heat transfer tubes 1. As described in embodiments 1 to 7, since the heat transfer tube 1 is formed with the extension portion 1B, the tube external heat transfer area Ao is larger than that of the conventional fin-tube heat exchanger. Therefore, the heat exchangers 20A and 20B according to embodiment 8 can improve heat exchange performance as compared with the conventional one.
In addition, in the heat exchanger 20B to which the heat transfer pipe 1 of embodiment 4 is applied, since the water guide passage for discharging dew condensation water is formed, the drainage can be improved. Further, by increasing the drainage, it is possible to improve the latent heat exchange performance or to shorten the defrosting operation time for removing frost from the heat exchanger 20B.
Embodiment 9
Next, embodiment 9 will be described. Embodiment 9 is similar to embodiment 8 in that the heat transfer tube 1 described in embodiments 1 to 7 is applied to a heat exchanger, and is different from embodiment 8 in that no fins are provided. In embodiment 9, the same reference numerals are given to the portions common to embodiments 1 to 8, and detailed description thereof is omitted.
Fig. 13 is a schematic diagram showing an example of the structure of the heat exchanger according to embodiment 9. Fig. 13 illustrates an example of a side surface of the heat exchanger 30 when viewed from the first direction. As shown in fig. 13, the heat exchanger 30 of embodiment 9 is configured by arranging a plurality of heat transfer tubes 1 described in embodiments 1 to 7, similarly to the heat exchangers 20A and 20B of embodiment 8.
The plurality of heat transfer pipes 1 are arranged in such a manner as to extend along the third direction. In embodiment 9, the heat exchanger 30 is disposed so that the third direction is parallel to the gravitational force. In addition, the plurality of heat transfer pipes 1 are arranged in parallel along the second direction. In other words, the plurality of heat transfer pipes 1 are arranged side by side in a direction perpendicular to both the flow direction of the first heat exchange fluid and the flow direction of the second heat exchange fluid. Headers 31A and 31B are connected to both ends of the heat transfer tube 1 in the third direction.
Here, in the heat exchanger 30, the fins 21 are not provided between the heat transfer tubes 1 adjacent to each other. Therefore, a space is formed between the adjacent heat transfer tubes 1. Therefore, when dew condensation occurs on the surface of the heat exchanger 30, drainage of the produced dew condensation water can be improved.
As described above, in the heat exchanger 30 according to embodiment 9, the heat exchange performance can be improved as compared with the conventional one, as in embodiment 8. The heat exchanger 30 according to embodiment 9 is configured such that the third direction, which is the flow direction of the first heat exchanger fluid, is parallel to gravity, and no fins are provided between the adjacent heat transfer tubes 1.
In this way, since the heat exchanger 30 does not have fins provided so as to be orthogonal to the gravitational direction, drainage of dew condensation water can be improved as compared with a fin-tube heat exchanger. Further, by increasing the drainage, it is possible to improve the latent heat exchange performance or to shorten the defrosting operation time for removing frost from the heat exchanger 30.
Description of the reference numerals
A heat transfer tube 1, a body 1A, an extension 1B, an outer wall 10, an outer wall overlapping portion 10A, an inner wall 11, an overlapping portion 11A, a partition 11B, a heat transfer promoting portion 12, heat transfer promoting portions 20A, 20B, 30 heat exchangers, 21 fins, 22 gaps, 31A, 31B headers.
Claims (10)
1. A heat transfer tube, wherein,
the heat transfer tube is provided with:
a flat body portion having a tube outer wall and a tube inner wall formed by bending one sheet material a plurality of times, and having a plurality of flow paths formed by being surrounded by the tube outer wall and the tube inner wall; and
an extension part formed by extending at least one end part of the plate material in a flat long axis direction indicating a long axis direction in a cross section of the main body part,
the extension portion is formed to extend from the tube outer wall in a direction horizontal to the flat long axis direction,
the length of the extension is longer than the length of the minor axis of the flat,
the body portion and the extension portion are formed by bending the one sheet material.
2. The heat transfer tube of claim 1, wherein,
an outer wall overlapping portion having a double structure is formed on the outer wall of the tube provided in the short axis direction of the flat tube.
3. The heat transfer tube of claim 2, wherein,
the outer wall overlapping part is more than 1/2 of the length of the flat short shaft.
4. A heat transfer tube according to any one of claims 1 to 3 wherein,
a portion of the tube outer wall is curved in a direction of a central axis of the flattened minor axis length.
5. A heat transfer tube according to any one of claims 1 to 3 wherein,
all of the tube outer walls are of a double or more construction.
6. A heat transfer tube according to any one of claims 1 to 3 wherein,
the outer tube wall and the inner tube wall are formed to be point-symmetrical at the intersection point of the central axes of the flat major axis length and the flat minor axis length.
7. A heat transfer tube according to any one of claims 1 to 3 wherein,
the extension has a heat transfer promoting portion that promotes heat transfer of a fluid flowing along an outer surface of the extension.
8. A heat transfer tube according to any one of claims 1 to 3 wherein,
the sheet material is coated with solder on both sides of the base material.
9. A heat exchanger, wherein,
the heat exchanger according to any one of claims 1 to 8,
the plurality of heat transfer tubes are arranged in parallel in a direction perpendicular to a flow direction of the first heat exchange fluid flowing through the plurality of flow paths and a flow direction of the second heat exchange fluid flowing through the outer surface of the main body,
no fins are provided between the heat transfer tubes adjacent to each other.
10. The heat exchanger of claim 9, wherein,
the heat exchanger is configured such that the direction of flow of the first heat exchange fluid is parallel to gravity.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2019/028190 WO2021009889A1 (en) | 2019-07-18 | 2019-07-18 | Heat-transfer tube and heat exchanger using the same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114072627A CN114072627A (en) | 2022-02-18 |
| CN114072627B true CN114072627B (en) | 2023-12-22 |
Family
ID=74210312
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980097777.5A Active CN114072627B (en) | 2019-07-18 | 2019-07-18 | Heat transfer tube and heat exchanger using the same |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP4001821B1 (en) |
| JP (1) | JP7262586B2 (en) |
| CN (1) | CN114072627B (en) |
| WO (1) | WO2021009889A1 (en) |
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| US2373218A (en) * | 1942-11-11 | 1945-04-10 | Modine Mfg Co | Oil cooler tube |
| JPS60185884U (en) * | 1984-05-22 | 1985-12-09 | 昭和アルミニウム株式会社 | Heat exchanger |
| JPS61198884U (en) * | 1985-05-27 | 1986-12-12 | ||
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| JP2018204919A (en) | 2017-06-09 | 2018-12-27 | カルソニックカンセイ株式会社 | Heat exchange tube and heat exchanger |
| CN110998201B (en) * | 2017-08-03 | 2022-02-11 | 三菱电机株式会社 | Heat exchanger and refrigeration cycle device |
| US11262132B2 (en) * | 2017-08-03 | 2022-03-01 | Mitsubishi Electric Corporation | Heat exchanger and refrigeration cycle apparatus |
| CN208296664U (en) * | 2018-05-17 | 2018-12-28 | 广东美的制冷设备有限公司 | Pipe wing monomer and heat exchanger, air conditioner with it |
| CN209310597U (en) * | 2018-12-18 | 2019-08-27 | 杭州三花微通道换热器有限公司 | Heat exchanger tube and heat exchanger with the heat exchanger tube |
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2019
- 2019-07-18 CN CN201980097777.5A patent/CN114072627B/en active Active
- 2019-07-18 EP EP19937853.0A patent/EP4001821B1/en active Active
- 2019-07-18 WO PCT/JP2019/028190 patent/WO2021009889A1/en unknown
- 2019-07-18 JP JP2021532632A patent/JP7262586B2/en active Active
Patent Citations (7)
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| JPH0396574U (en) * | 1989-12-29 | 1991-10-02 | ||
| JPH09159386A (en) * | 1995-12-13 | 1997-06-20 | Sanden Corp | Multiple pipe heat exchanger |
| JPH10206053A (en) * | 1997-01-21 | 1998-08-07 | Toyo Radiator Co Ltd | Tubes for heat exchanger |
| JP2000227293A (en) * | 1999-02-05 | 2000-08-15 | Zexel Corp | Heat exchanger and its manufacture |
| KR100378055B1 (en) * | 2000-12-21 | 2003-03-29 | 만도공조 주식회사 | Coolant tube of heat exchanger and processing method thereof |
| EP3096102A1 (en) * | 2015-05-22 | 2016-11-23 | Delphi Automotive Systems Luxembourg SA | Flat tube for a heat exchanger |
| WO2019026239A1 (en) * | 2017-08-03 | 2019-02-07 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2021009889A1 (en) | 2021-11-25 |
| EP4001821A1 (en) | 2022-05-25 |
| CN114072627A (en) | 2022-02-18 |
| JP7262586B2 (en) | 2023-04-21 |
| WO2021009889A1 (en) | 2021-01-21 |
| EP4001821B1 (en) | 2024-03-06 |
| EP4001821A4 (en) | 2022-07-06 |
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