WO2007091561A1 - フィンチューブ型熱交換器 - Google Patents
フィンチューブ型熱交換器 Download PDFInfo
- Publication number
- WO2007091561A1 WO2007091561A1 PCT/JP2007/052032 JP2007052032W WO2007091561A1 WO 2007091561 A1 WO2007091561 A1 WO 2007091561A1 JP 2007052032 W JP2007052032 W JP 2007052032W WO 2007091561 A1 WO2007091561 A1 WO 2007091561A1
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- WO
- WIPO (PCT)
- Prior art keywords
- cut
- raised
- fin
- flow direction
- heat exchanger
- Prior art date
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Classifications
-
- 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
- F28D1/047—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 bent, e.g. in a serpentine or zig-zag
- F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
- F28F1/325—Fins with openings
Definitions
- the present invention relates to a finned tube heat exchanger.
- fin tube type heat exchange is often used in, for example, an air conditioner, a refrigerator / refrigerator, a dehumidifier, and the like.
- the fin tube type heat exchange is constituted by a plurality of fins arranged at predetermined intervals and a heat transfer tube passing through the fins.
- Fin tube heat exchangers are known in which fin shapes are devised for the purpose of promoting heat transfer. For example, heat exchange with many pins provided on the fin surface is known. In this heat exchange, the flow on the fin surface side is stirred by these pins, and heat exchange is promoted.
- Japanese Laid-Open Patent Publication No. 2001-116488 discloses a fin tube type heat exchanger having a plurality of slit-like cuts (hereinafter referred to as slit portions) formed on a plate base surface.
- slit portions a fin tube type heat exchanger having a plurality of slit-like cuts (hereinafter referred to as slit portions) formed on a plate base surface.
- the slit portion is formed by press-molding the fin so that a part of the fin is cut and raised in a slit shape.
- slit fins In fins having slit portions (hereinafter referred to as slit fins), heat transfer is promoted based on the following principle. That is, as shown in FIG. 12A, in the fin (smooth fin) 100 in which the slit portion is not provided, when air A is supplied from the front, the fin 100 has a continuous force from the front edge 100a toward the rear. A temperature boundary layer BL is generated. The temperature boundary layer BL is thin in the vicinity of the leading edge 100a, but becomes thicker toward the rear. On the other hand, as shown in FIG. 12B, in the slit fin 101, the temperature boundary layer BL is also generated from the front edge 102a of each slit portion 102 connected only by the front edge 101a of the fin 101.
- the temperature boundary layer BL developed from the leading edge 101a of 101 can be divided, and the temperature boundary layer BL can be generated intermittently. Therefore, in the slit fin 101, the average thickness of the temperature boundary layer BL is thinner than that of the smooth fin 100. As a result, the heat transfer coefficient is improved.
- the present invention has been made in view of the strong point, and an object of the present invention is to provide a fin tube that can improve the heat transfer coefficient more than the conventional one while maintaining the ease of manufacturing. To provide heat exchange.
- a finned tube heat exchanger includes a plurality of fins arranged in parallel at intervals, and a plurality of heat transfer tubes that penetrate the fins, and flows on the surface side of the fins.
- a fin-tube heat exchanger for exchanging heat between a first fluid and a second fluid flowing inside the heat transfer tube, wherein each fin includes a part of the first fluid.
- a cut-and-raised part is formed which is cut and raised as if it was turned from the upstream side to the downstream side in the flow direction, and the cross-sectional shape is tapered toward the upstream side. It is something to be struck.
- the cross-sectional shape of the cut and raised portion may be a semicircular shape.
- the cut-and-raised portion may have a semi-elliptical cross-sectional shape.
- the cross-sectional shape of the cut-and-raised portion may be a semi-elliptical shape that is elongated toward the upstream side.
- the cross-sectional shape of the cut and raised portion may be a wedge shape.
- a plurality of the cut-and-raised portions are provided along the flow direction of the first fluid, and the cut-and-raised portions adjacent to each other in the flow direction are cut and raised in directions opposite to each other with the fin as a boundary. Also good.
- the cut and raised height of the cut and raised portion may be 1Z2 or less of the fin pitch.
- the cut-and-raised portion is provided in a plurality along the flow direction of the first fluid.
- the sum of the lengths of the cut-and-raised portions in the flow direction of the fluid may be 1Z2 to 2Z3 of the length of the fins in the flow direction of the first fluid.
- a plurality of the raised portions are provided along the flow direction of the first fluid, and the number of the raised portions along the flow direction may be 3 or less per one heat transfer tube. Good
- the cut-and-raised part is provided in plural along the flow direction of the first fluid, and the length of the cut-and-raised part located on the most upstream side in the flow direction is the flow of the other raised parts. It may be longer than the direction length.
- the fin may be configured such that the upstream side in the flow direction of the first fluid is longer than the downstream side with respect to the center of the heat transfer tube.
- a cut-and-raised portion is formed in the fin, and the cross-sectional shape of the cut-and-raised portion is tapered toward the upstream side in the flow direction. It is curved or bent to be. Therefore, the temperature boundary layer of the fluid in the cut and raised portion can be thinned. Therefore, it is possible to improve the heat transfer coefficient more than before while maintaining the ease of manufacture.
- FIG. 1 Perspective view of finned tube heat exchanger
- FIG. 3A is an enlarged view of the main part of the finned tube heat exchanger according to Embodiment 1.
- FIG. 3B is an enlarged view of the main part of a finned tube heat exchanger according to a modification of Embodiment 1 (III III sectional view).
- FIG. 3D Cross-sectional view of a variation of the cut-and-raised part
- FIG. 5A Conceptual diagram showing heat transfer in slit fins
- FIG. 5B is a conceptual diagram showing heat transfer in the fin according to the embodiment.
- FIG. 7 is an enlarged view of the main part of the finned tube heat exchanger according to the second embodiment.
- Figure 8A Illustration of ellipticity
- FIG. 8B Diagram showing the relationship between ellipticity, average heat transfer coefficient and pressure loss
- FIG. 9 is a cross-sectional view of the cut-and-raised part of the finned tube heat exchanger according to the third embodiment.
- FIG. 11A is a partial elevation view of a finned tube heat exchanger according to another embodiment.
- FIG. 11B Xlb—Xlb cross-sectional view of Fig. 11A
- the finned tube heat exchanger 1 includes a plurality of fins 3 arranged in parallel at predetermined intervals, and a plurality of heat transfer tubes 2 penetrating these fins 3. ing.
- the fluid flowing inside the heat transfer tube 2 and the surface side of the fin 3 (the outer surface of the heat transfer tube 2 is exposed, in this case, the surface of the fin 3 and the outer surface of the heat transfer tube 2 In the case where is exposed, the fluid flowing through the fin 3 and the surface of the heat transfer tube 2) exchanges heat.
- air A flows on the surface side of the fin 3, and cooling medium B flows inside the heat transfer tube 2.
- the fluid flowing inside the heat transfer tube 3 and the fluid flowing on the surface side of the fin 3 are not particularly limited. These fluids may be gas or liquid.
- the fins 3 are formed in a rectangular flat plate shape, and are arranged along the Y direction shown in the figure. Note that in the present embodiment, the fins 3 are arranged at a constant interval, and the intervals may not necessarily be constant.
- a punched aluminum plate having a thickness of 0.08-0.2 mm can be preferably used. From the viewpoint of improving the fin efficiency, the thickness of the fin 3 is particularly preferably 0.1 mm or more.
- the surface of the fin 3 is subjected to a hydrophilic treatment such as boehmite treatment or application of a hydrophilic paint.
- the heat transfer tubes 2 are arranged along the longitudinal direction of the fins 3 (hereinafter also referred to as the Z direction). Are lined up. However, the heat transfer tubes 2 do not necessarily need to be arranged in a line along the Z direction, and may be arranged in a staggered manner, for example.
- the outer diameter D (see FIG. 2) of the heat transfer tube 2 is, for example, 1 to 20 mm, and may be 4 mm or less.
- the heat transfer tube 2 is in close contact with the fin collar of the fin 3 (not shown. In FIG. 2 and the like, illustration of the fin collar is omitted) by expanding the tube. Is fitted.
- the heat transfer tube 2 may be a smooth tube having a smooth inner surface or a grooved tube.
- the heat exchanger 1 is installed in such a posture that the flow direction of the air A (the X direction in FIG. 1) is almost perpendicular to the Y direction and the Z direction. However, as long as a sufficient amount of heat exchange can be ensured, the airflow direction may be slightly inclined from the X direction!
- the center line C2 of the heat transfer tube 2 is shifted from the center line C1 of the fin 3 to the downstream side (right side in FIG. 2) in the airflow direction. Therefore, when the center line C2 of the heat transfer tube 2 is used as a reference, the fin 3 is longer on the upstream side (left side in FIG. 2) than on the downstream side. As described above, the front edge of the fin 3 has a large local heat transfer coefficient. On the other hand, the rear of the heat transfer tube 2 is a dead water area, and the local heat transfer coefficient is small. Therefore, according to the present heat exchanger 1, the front edge of the fin 3 is extended forward, and the rear edge of the fin 3 is shortened. The area of the portion with a small heat transfer coefficient can be reduced.
- the fin 3 has a first cut-and-raised portion 5a, a second cut-and-raised portion 5b, and a third cut in order from the upstream side to the downstream side of the airflow A.
- a raised portion 5c is formed.
- the first to third cut-and-raised portions 5a to 5c are respectively formed between the adjacent heat transfer tubes 2, and a plurality of sets are provided along the Z direction.
- Each cut-and-raised portion 5a to 5c is a portion of the fin 3 that is cut and raised as if it is turned from the upstream side toward the downstream side.
- the cross section of each cut-and-raised portion 5a to 5c (cross section orthogonal to the Z direction) is tapered toward the upstream side.
- the cross-sectional shape of the cut and raised portions 5a to 5c is formed in a semicircular shape.
- the diameter of the semicircle formed by the cross sections of the cut and raised portions 5a to 5c is, for example, 0.2 to 1. Omm.
- the shapes of the cut-and-raised portions 5a to 5c can be specified as follows.
- the direction in which the fins 3 are arranged (cut and raised, the thickness direction of the part) is the height direction HL, and the cross section parallel to the height direction HL and the flow direction AL (air flow direction) of air A is finned. It is defined as 3 cross section.
- the cut-and-raised portion 5a (5b, 5c) is bent so that the cut-and-raised tip 5t is separated from the surface of the fin 3 and the cut-and-raised tip 5t is inverted downstream. Then, as shown by the dotted line region in FIG.
- the height h of the space SH it is not necessary for the height h of the space SH to decrease monotonically as it goes upstream in the airflow direction AL. If it contains, it is enough. For example, as shown in FIG. 3D, the cut is made so that the space SH shows the maximum height hmax at a position advanced a predetermined distance from the position of the downstream end 5t (cutting tip 5t) to the upstream side in the airflow direction AL.
- the shape of the raising part 5a (5b, 5c) may be adjusted.
- a plurality of cut-and-raised portions 5a to 5c are provided along the flow direction of air A, and the plurality of cut-and-raised portions 5a to 5c are respectively long in the flow direction of air A.
- the dimensions are adjusted so that the length in the arrangement direction of the plurality of heat transfer tubes 2 is larger. That is, the direction parallel to the in-plane direction of the fin 3 and the arrangement direction of the plurality of heat transfer tubes 3 can be defined as the longitudinal direction of the plurality of raised portions 5a to 5c.
- the length UL2 in the longitudinal direction (Z direction) of the second cut and raised portion 5b is equal to the length in the longitudinal direction of the third cut and raised portion 5c.
- the longitudinal length UL1 of the first cut-and-raised portion 5a is longer than the longitudinal length UL2 of the second cut-and-raised portion 5b.
- the longitudinal length UL1 of the first cut and raised portion 5a is twice the longitudinal length UL2 of the second cut and raised portion 5b.
- the longitudinal lengths of the first to third cut-and-raised portions 5a to 5c may be equal to each other or may be different from each other.
- the longitudinal direction UL1 of the first cut-and-raised portion 5a is larger than the distance PG between the adjacent heat transfer tubes 2 and smaller than the center-to-center distance PP between the adjacent heat transfer tubes 2.
- the length UL2 in the longitudinal direction of the second cut-and-raised portion 5b and the third cut-and-raised portion 5c is smaller than the above-mentioned interval PG which is larger than 1Z2 of the interval PG.
- the first to third cut-and-raised portions 5a to 5c are formed so that the directions of the cut-and-raised are different from each other.
- the first cut and raised portion 5a is cut and raised on the upper side of FIG. 3A
- the second cut and raised portion 5b is cut and raised on the lower side
- the third cut and raised portion 5c is cut and raised on the upper side.
- the cut-and-raised portions adjacent to each other in the airflow direction are reversed in the direction of the cut-and-raised with respect to the fin 3 (specifically, the portion where the fin 3 is cut and raised).
- the lengths (full lengths) UH in the airflow direction of the first to third cut-and-raised portions 5a to 5c are equal to each other.
- the total length UH of the first to third cut and raised portions 5a to 5c may not necessarily be the same, but may be different from each other.
- the total length UH of the first to third cut and raised portions 5a to 5c may be gradually shortened or gradually lengthened.
- the cut and raised heights UW of the first to third cut and raised portions 5a to 5c are also equal to each other.
- the cut-and-raised height UW is the distance from the center of the fin 3 in the thickness direction.
- the cut and raised height UW is preferably 1Z2 or less of the fin pitch FP.
- the cut-and-raised height UW is 1Z2 or less of the fin pitch FP, when the heat exchanger 1 is viewed from the upstream side to the downstream side of the airflow (as viewed in the X direction), the adjacent fins 3 are cut and raised. This is because the portions 5a to 5c do not overlap and increase in pressure loss can be suppressed.
- the length UH force in the air flow direction of the first cut-and-raised part 5a which is the cut-and-raised part located on the most upstream side, is the second and third cut-and-raised parts that are the other raised parts.
- the length of the strain sections 5b and 5c in the air flow direction is longer than Uh.
- the cut and raised height UW of the first cut and raised portion 5a is higher than the cut and raised height Uw of the second and third cut and raised portions 5b and 5c.
- the length UH of the cut-and-raised portions 5a to 5c in the flow direction of the air A is referred to as the airflow direction length UH of the cut-and-raised portions 5a to 5c.
- the length UH of the cut-and-raised part 5a to 5c in the air flow direction corresponds to the upstream end force of the opening generated by forming the cut-and-raised parts 5a to 5c, as shown in FIG.
- FIG. 4 shows the temperature boundary layer BL in the first cut and raised portion 5a.
- the first cut-and-raised portion 5a has a tapered cross-sectional shape that is directed toward the upstream side, so that the air flows thinly along the surface of the first cut-and-raised portion 5a. The thickness of the temperature boundary layer BL is reduced.
- the temperature boundary layer BL expands as it goes backward, but the first cut-and-raised part 5a is formed in a shape that expands backward as it goes. Therefore, the temperature boundary layer BL is kept thin not only at the front edge of the first cut and raised portion 5a but also at the rear side. Therefore, the heat transfer coefficient of the first cut-and-raised portion 5a is dramatically improved.
- the shape (outer shape) of the plurality of raised portions 5a to 5c has a longitudinal shape (for example, a rectangular shape, Or the trapezoidal shape in which the long side and the short side are orthogonal to the airflow direction), and the directions of the plurality of raised portions 5a to 5c are aligned so that the longitudinal direction is orthogonal to the airflow direction.
- a longitudinal shape for example, a rectangular shape, Or the trapezoidal shape in which the long side and the short side are orthogonal to the airflow direction
- the directions of the plurality of raised portions 5a to 5c are aligned so that the longitudinal direction is orthogonal to the airflow direction.
- the heat is supplied to the slit portion 102 through the root 102 c of the slit portion 102.
- the root 102c extends in a direction orthogonal to the longitudinal direction of the slit portion 102, the width SW of the root 102c is small. Therefore, in the slit fin 101, the heat supply path to the slit portion 102, which is the heat transfer promoting portion, is narrow. Therefore, although the slit portion 102 has a high local heat transfer coefficient, it is difficult to say that the heat supply is necessarily sufficient.
- this heat exchange l (fin 3) as shown in FIG.
- the root 10 of the cut-and-raised part 5 extends in the longitudinal direction of the cut-and-raised part 5 (vertical direction in FIG. 5B). 10 width UL is wide. Therefore, a sufficient amount of heat is supplied to the cut and raised portion 5. Therefore, according to the present heat exchanger 1 (fin 3), the heat exchange performance can be improved also in terms of the amount of heat supplied to the heat transfer promoting part.
- the cut-and-raised portions 5a to 5c are formed in a semicircular cross-sectional shape, and the airflow in the cut-and-raised portions 5a to 5c is shown in FIG.
- the width in the direction perpendicular to the direction increases from the upstream side to the downstream side, and is maximum at the downstream ends of the cut-and-raised portions 5a to 5c.
- the downstream end of the cut-and-raised portion refers to the tip of the cut-and-raised portion (see reference numeral 5t in FIG. 3A).
- the downstream portion becomes a dead water area, and the heat transfer coefficient of the downstream portion becomes low.
- the cut-and-raised portions 5a to 5c of the present embodiment since the cross section is semicircular, the dead water area can be reduced. Accordingly, the heat transfer coefficient can be effectively improved.
- cut-and-raised portions 5a to 5c may be tapered toward the upstream side, but in particular in the present embodiment, the cut-and-raised portions 5a to 5c are formed in a semicircular shape. . Therefore, the development of the boundary layer can be further suppressed, and the heat transfer coefficient can be further improved.
- the cut-and-raised portions adjacent to each other in the airflow direction are opposite to each other. Therefore, the second cut and raised portion 5b is not easily affected by the temperature boundary layer of the first cut and raised portion 5a, and the third cut and raised portion 5c is not easily affected by the temperature boundary layer of the second cut and raised portion 5b. . Therefore, the heat transfer coefficient of the second cut and raised portion 5b and the third cut and raised portion 5c can be further improved.
- the cut-and-raised height UW of the cut-and-raised portions 5a to 5c is set to 1Z2 or less of the fin pitch FP. Therefore, it is possible to prevent the pressure loss from increasing significantly. However, depending on the application of heat exchange, etc., an increase in pressure loss may be allowed. In such a case, the cut and raised height UW is H It may be larger than 1Z2 of FP.
- the lower limit of the cut-and-raised height UW of the cut-and-raised portions 5a to 5c is not particularly limited. For example, it should be 1Z5 or more of the fin pitch FP (however, the thickness of the fin 3 is more than twice the thickness FT). it can.
- the heat transfer rate increases as the number of cut-and-raised portions increases, but the rate of increase gradually decreases.
- the larger the number of raised parts the more complicated the production and the greater the pressure loss.
- the number of the cut-and-raised portions 5a to 5c along the airflow direction is three (a plurality).
- the ratio of the airflow direction length UH of the cut-and-raised portions 5a to 5c to the airflow direction length L of the fin 3 can be varied depending on the number of rows of the heat transfer tubes 2.
- the ratio described above is a ratio when the heat transfer tubes 2 penetrating the fins 3 are in one row.
- the number of cut-and-raised portions 5a to 5c is also the number when the heat transfer tubes 2 penetrating the fins 3 are in one row.
- the first cut and raised portion 5a located on the most upstream side has a relatively high heat transfer coefficient.
- the length in the longitudinal direction of the first cut-and-raised portion 5a is larger than the length in the longitudinal direction of the other cut-and-raised portions 5b and 5c. For this reason, the area of the portion having a large heat transfer coefficient is increased, so that the heat transfer coefficient can be effectively improved.
- the speed boundary layer of the cut-and-raised portions 5a to 5c becomes thin, so even if condensation occurs on the surface of the fin 3, the water film tends to be thin. For this reason, even if condensation occurs, the effect of promoting heat transfer is unlikely to decrease, and pressure loss is unlikely to increase.
- the cut-and-raised portions 5a to 5c are formed in a semicircular cross-sectional shape.
- the cross-sectional shape of the cut-and-raised portions 5a to 5c is not limited to a semicircular shape.
- the cross-sectional shapes of the cut-and-raised portions 5a to 5c are semi-elliptical.
- the fin 3 of the heat exchanger 1 according to the second embodiment has the cut-and-raised portion 5a that is cut and raised so that a part of the fin 3 is turned from the upstream side toward the downstream side.
- ⁇ 5c are formed, and the cut-and-raised portions 5a to 5c are formed in a semi-elliptical shape so that the cross-sectional shape is curved toward the upstream side and becomes tapered. Since other configurations are the same as those of the first embodiment, description thereof is omitted.
- the ellipticities of the cut and raised portions 5a to 5c may be different from each other.
- Fig. 8B shows the simulation results of surface average heat transfer coefficient and pressure loss versus ellipticity.
- the cross-sectional shape of the cut-and-raised portions 5a to 5c is tapered toward the upstream side. Therefore, as in Embodiment 1, the temperature boundary layer in the cut-and-raised portions 5a to 5c can be made thin, so that the heat transfer coefficient can be improved. Furthermore, in this embodiment, the cross-sectional shape of the cut-and-raised portions 5a to 5c is formed in a semi-elliptical shape. Therefore, pressure loss can be reduced as compared with the first embodiment.
- the cut-and-raised portions 5a to 5c are formed such that the major axis direction of the transverse section is parallel to the airflow direction. Therefore, the pressure loss can be further reduced.
- the ellipticity of the cut-and-raised portions 5a to 5c is set to be greater than 0.33 and less than 1, the cross-section of the cut-and-raised portions 5a to 5c is larger than that of a semicircular shape.
- the pressure loss can be reduced while keeping the heat transfer coefficient equal to or higher.
- the cross-sectional shapes of the cut-and-raised portions 5a to 5c are formed in a wedge shape.
- the fin 3 of the heat exchanger 1 according to Embodiment 3 has a cut-and-raised portion 5a that is cut and raised so that a part of the fin 3 is turned from the upstream side to the downstream side. ⁇ 5c are formed, and the cut-and-raised portions 5a to 5c are curved and formed in a wedge shape so that the cross-sectional shape is tapered toward the upstream side.
- the wedge shape is a shape that continues to spread from the front end to the rear end. Since other configurations are the same as those of the first embodiment, description thereof is omitted.
- the temperature in the cut-and-raised portions 5a to 5c is the same as in the first embodiment.
- the boundary layer can be thinned. Therefore, the heat transfer rate can be improved.
- the cut-and-raised portions 5a to 5c continue to expand to the rear end of the front end force, so that the temperature boundary layer can also be thinned at the rear ends of the cut-and-raised portions 5a to 5c. Therefore, the heat transfer rate can be further improved.
- the front ends of the cut and raised portions 5a to 5c are rounded.
- the front ends of the cut and raised portions 5a to 5c are not necessarily rounded. As shown in FIG. It may be sharp.
- the cross sections of the cut and raised portions 5a to 5c may be formed in a bent shape.
- the cross section of the front edge portion of the fin 3 is formed in a semi-rectangular shape.
- the front edge portion of the fin 3 may have a semicircular shape, a semi-elliptical shape, or a wedge shape as in the cut-and-raised portions 5a to 5c.
- the number of rows of the heat transfer tubes 2 may be two or more.
- the fins 3 may be a single unit common to each row or may be a fin divided for each row.
- the first row fins and the second row fins may be separated.
- the fins in the first row and the fins in the second row may be shifted and the fins 3 in the second row may be positioned between the fins 3 in the first row.
- the present invention is useful for a finned tube heat exchanger.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/278,360 US9086243B2 (en) | 2006-02-06 | 2007-02-06 | Fin-tube heat exchanger |
CN2007800046569A CN101379361B (zh) | 2006-02-06 | 2007-02-06 | 翅片管式换热器 |
EP20070713861 EP1985958A4 (en) | 2006-02-06 | 2007-02-06 | RIB TUBE HEAT EXCHANGERS |
JP2007525096A JP4022250B2 (ja) | 2006-02-06 | 2007-02-06 | フィンチューブ型熱交換器 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006028062 | 2006-02-06 | ||
JP2006-028062 | 2006-02-06 |
Publications (1)
Publication Number | Publication Date |
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WO2007091561A1 true WO2007091561A1 (ja) | 2007-08-16 |
Family
ID=38345157
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/052032 WO2007091561A1 (ja) | 2006-02-06 | 2007-02-06 | フィンチューブ型熱交換器 |
Country Status (5)
Country | Link |
---|---|
US (1) | US9086243B2 (ja) |
EP (1) | EP1985958A4 (ja) |
JP (1) | JP4022250B2 (ja) |
CN (1) | CN101379361B (ja) |
WO (1) | WO2007091561A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2015017776A (ja) * | 2013-07-12 | 2015-01-29 | 株式会社デンソー | 熱交換器用フィン |
Families Citing this family (12)
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US9303882B2 (en) | 2009-06-26 | 2016-04-05 | Trane International Inc. | Blow through air handler |
US10103089B2 (en) | 2010-03-26 | 2018-10-16 | Hamilton Sundstrand Corporation | Heat transfer device with fins defining air flow channels |
KR101882020B1 (ko) * | 2012-08-01 | 2018-07-25 | 엘지전자 주식회사 | 열교환기 |
KR20140017835A (ko) * | 2012-08-01 | 2014-02-12 | 엘지전자 주식회사 | 열교환기 |
JP6710205B2 (ja) * | 2015-05-29 | 2020-06-17 | 三菱電機株式会社 | 熱交換器及び冷凍サイクル装置 |
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CN107289807A (zh) * | 2017-07-06 | 2017-10-24 | 贺迈新能源科技(上海)有限公司 | 改变翅片穿管换热器翅片间距的装置及翅片穿管换热器 |
JP7209487B2 (ja) * | 2017-11-24 | 2023-01-20 | Maアルミニウム株式会社 | ろう付け処理後の親水性に優れるアルミニウムフィン及び熱交換器とその製造方法 |
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Also Published As
Publication number | Publication date |
---|---|
JP4022250B2 (ja) | 2007-12-12 |
EP1985958A1 (en) | 2008-10-29 |
JPWO2007091561A1 (ja) | 2009-07-02 |
US9086243B2 (en) | 2015-07-21 |
CN101379361B (zh) | 2010-07-21 |
US20090050303A1 (en) | 2009-02-26 |
CN101379361A (zh) | 2009-03-04 |
EP1985958A4 (en) | 2012-09-19 |
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