EP2843345B1 - Fin-tube heat exchanger and refrigeration cycle device using same - Google Patents
Fin-tube heat exchanger and refrigeration cycle device using same Download PDFInfo
- Publication number
- EP2843345B1 EP2843345B1 EP13781555.1A EP13781555A EP2843345B1 EP 2843345 B1 EP2843345 B1 EP 2843345B1 EP 13781555 A EP13781555 A EP 13781555A EP 2843345 B1 EP2843345 B1 EP 2843345B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fin
- cut
- raised
- raised part
- heat exchanger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
- The present invention especially relates to a fin-tube heat exchanger used for heat exchange of refrigerant.
- As shown in
Fig. 17 , a conventional fin-tube heat exchanger of this kind is composed of a plurality offins 1 arranged at predetermined intervals Fp from one another, andheat transfer pipes 2 inserted into thefins 1 substantially at right angles. -
Fig. 18 (a) is a sectional view when fins configuring the conventional fin-tube heat exchanger are laminated on one another, andFig. 18 (b) is a partial plan view of fins configuring the conventional fin-tube heat exchanger. - As shown in
Figs. 18 , afin collar 3 rising from a surface of thefin 1 is formed on each of thefins 1, and theheat transfer pipe 2 is inserted into thefin collar 3. Anend surface 30 of thefin collar 3 comes into contact withadjacent fins 1 and holds a predetermined distance between thefins 1. - Air current 100 (e.g., air) is introduced into the fin-tube heat exchanger by an air blower (not shown). The
air current 100 flows through gaps between the laminatedfins 1 and exchanges heat with fluid (e.g., refrigerant such as R410a and carbon dioxide) flowing through theheat transfer pipe 2. - Generally, fluid flowing through the
heat transfer pipe 2 is in a two-phase state of a liquid phase and a gas phase. The liquid phase of the fluid evaporates by the heat exchange with theair current 100, and the liquid becomes overheated gas and flows out from the fin-tube heat exchanger. - In some cases, to facilitate the heat transfer for enhancing the efficiency in such a fin-tube heat exchanger, a cut-and-raised
part 4 is formed over the entire region of each of thefin 1 as shown inFigs. 19 (seepatent documents -
Fig. 19 (a) is a sectional view when fins configuring the fin-tube heat exchanger described inpatent document 1 are laminated on one another, andFig. 19(b) is a partial plane view of the fin configuring the fin-tube heat exchanger described inpatent document 1. - The cut-and-raised
parts 4 shown inFigs. 19 have a louver shape formed by bending a portion of thefin 1 substantially perpendicularly to a finflat surface 1c. The cut-and-raisedparts 4 are inclined such that they are arranged on thefin 1 straightly from an upstream side to a downstream side of theair current 100, thereby reducing a dead water region which is generated in wake flow of theheat transfer pipe 2. -
Fig. 20(a) is a sectional view when fins configuring a fin-tube heat exchanger described inpatent document 2 are laminated on one another, andFig. 20(b) is a partial plane view of the fin configuring the fin-tube heat exchanger described inpatent document 2. - Cut-and-raised
parts 4 shown inFigs. 20 are offset from each other such that flat surfaces of the cut-and-raisedparts 4 are substantially in parallel to a finflat surface 1c, and both ends of the cut-and-raisedpart 4 are connected to the finflat surface 1c to form a slit. The cut-and-raisedparts 4 are formed on theheat transfer pipe 2 on both upstream side and downstream side of theair current 100. A height of the cut-and-raisedpart 4 is set in a predetermined range. The fin-tube heat exchanger described inpatent document 2 is provided with the cut-and-raisedparts 4 shown inFigs. 20 . According to this, extreme deterioration in transfer performance caused when frost is formed is suppressed. -
Fig. 21(a) is a sectional view when fins configuring a fin-tube heat exchanger described inpatent document 3 are laminated on one another, andFig. 21(b) is a partial plane view of the fin configuring the fin-tube heat exchanger described inpatent document 3. - Cut-and-raised
parts 4 shown inFigs. 21 have a louver shape formed by bending a portion of thefin 1 substantially perpendicularly to a finflat surface 1c. The cut-and-raisedpart 4 formed by bending the fin 1 form a cut-and-raisedpart openings 4c towardadjacent fins 1. - The cut-and-raised
part 4 is placed on thefin 1 such that the cut-and-raisedpart 4 inclines with respect to a flowing direction of theair current 100, and the cut-and-raisedpart 4 intersects with the finflat surface 1c as viewed from a direction perpendicular to the finflat surface 1c. As a result, turbulence flow is promoted by collision betweenair currents 100 generated when theair current 100 passes through the cut-and-raisedpart openings 4c, and heat transfer of the fin-tube heat exchanger is promoted. -
JP-A 2001091101 claim 1. -
- [Patent Document 1] Japanese Patent Application Laid-open No.
2008-89237 - [Patent Document 2] Japanese Patent Application Laid-open No.
H11-125495 - [Patent Document 3] Japanese Patent Application Laid-open No.
2007-309533 - According to the conventional configurations, however, since the cut-and-raised
parts 4 are formed over the entire region of thefin 1. Therefore, much frost is formed on thefin 1 especially on the upstream side of theair current 100 of thefin 1 where heat is actively exchanged, and there is a problem that heat transfer performance is deteriorated. - Further, in the conventional configuration, water precipitated by the fin 1 stays at the cut-and-raised
part 4 and does not smoothly flow down, and there is a problem that the heat transfer performance is deteriorated. - The present invention has been accomplished to solve the conventional problems, and it is an object of the invention to provide a fin-tube heat exchanger which reduces frost formed on a fin, which enhances drainage performance and which has excellent heat transfer performance.
- To solve the conventional problems, the present invention provides a fin-tube heat exchanger according to
claim 1 including a plurality of fins which have cut-and-raised parts and through which air current passes, and a plurality of heat transfer pipes which penetrate the plurality of fins and through which fluid flows, wherein the cut-and-raised parts are placed only on a downstream side of a center of the closest heat transfer pipe with respect to the air current, and the cut-and-raised parts incline with respect to the air current. - According to this, the cut-and-raised part is provided only on the downstream side of the air current where frost is less prone to be formed, and it is possible to reduce the frost formation. Further, since water on the fin can be made to smoothly flow by the cut-and-raised part which inclines with respect to the air current direction, it is possible to enhance the drainage performance.
- According to the present invention, it is possible to provide a fin-tube heat exchanger in which an amount of formed frost is small, drainage performance is enhanced, and heat transfer performance is excellent.
-
-
Fig. 1(a) is a sectional view when fins of a fin-tube of the heat exchanger in a first embodiment of the present invention are laminated on one another, andFig. 1(b) is a partial plane view of the fin of the fin-tube heat exchanger; -
Fig. 2 is a partial plan view showing a positional relation between a cut-and-raised part and a heat transfer pipe in a fin of the fin-tube heat exchanger; -
Fig. 3 is a sectional view showing a height Hs of the cut-and-raised part and a height Hw of a waveform in the fin of the fin-tube heat exchanger; -
Fig. 4 is a sectional view showing the height Hs of the cut-and-raised part and a height Hc of a fin collar in the fin of the fin-tube heat exchanger; -
Fig. 5 is an explanatory diagram of a drainage operation in the fin of the fin-tube heat exchanger; -
Fig. 6 (a) is a sectional view when fins of different shape of a fin-tube heat exchanger in a second embodiment of the invention are laminated on one another, andFig. 6(b) is a partial plane view of the fin of different shape of the fin-tube heat exchanger; -
Fig. 7 (a) is a sectional view when fins of different shape of a fin-tube heat exchanger in a third embodiment of the invention are laminated on one another, andFig. 7(b) is a partial plane view of the fin of different shape of the fin-tube heat exchanger; -
Fig. 8 is a partial plan view of a fin of a fin-tube heat exchanger in a fourth embodiment of the invention -
Fig. 9(a) is a sectional view when fins of a fin-tube heat exchanger in a fifth embodiment of the invention are laminated on one another, andFig. 9 (b) is a partial plane view of the fin of the fin-tube heat exchanger; -
Fig. 10 is a partial plane view of the fin showing a relation between a cut-and-raised part and isotherm of a fin in the fin of the fin-tube heat exchanger; -
Fig. 11 is a sectional view showing a height Hs of the cut-and-raised part and a height Hw of a waveform in the fin of the fin-tube heat exchanger; -
Fig. 12 is a sectional view showing a height Hs of the cut-and-raised part and a height Hc of the fin collar in the fin of the fin-tube heat exchanger; -
Fig. 13 is an explanatory diagram of a drainage operation in the fin of the fin-tube heat exchanger; -
Fig. 14(a) is a sectional view when fins of different shape of a fin-tube heat exchanger in a sixth embodiment of the invention are laminated on one another, andFig. 14 (b) is a partial plane view of the fin of different shape of the fin-tube heat exchanger; -
Fig. 15(a) is a sectional view when fins of different shape of a fin-tube heat exchanger in a seventh embodiment of the invention are laminated on one another, andFig. 15 (b) is a partial plane view of the fin of different shape of the fin-tube heat exchanger; -
Fig. 16 is a partial plane view of fins of a fin-tube heat exchanger in an eighth embodiment of the invention; -
Fig. 17 is a diagram showing a configuration of a conventional fin-tube heat exchanger; -
Fig. 18(a) is a sectional view when fins of the conventional fin-tube heat exchanger are laminated on one another, andFig. 18(b) is a partial plane view of the fin of the fin-tube heat exchanger; -
Fig. 19(a) is a sectional view when fins of different shape of another conventional fin-tube heat exchanger are laminated on one another, andFig. 19(b) is a partial plane view of the fin of different shape of the fin-tube heat exchanger; -
Fig. 20(a) is a sectional view when fins of different shape of another conventional fin-tube heat exchanger are laminated on one another, andFig. 20(b) is a partial plane view of the fin of different shape of the fin-tube heat exchanger; -
Fig. 21(a) is a sectional view when fins of different shape of another conventional fin-tube heat exchanger are laminated on one another, andFig. 21(b) is a partial plane view of the fin of different shape of the fin-tube heat exchanger. -
- 1
- fin
- 1a
- fin windward portion
- 1b
- fin leeward portion
- 1c
- fin flat surface
- 2
- heat transfer pipe
- 3
- fin collar
- 4
- cut-and-raised part
- 4a
- cut-and-raised side
- 4b
- raised side
- 4c
- cut-and-raised part opening
- 5
- corrugated portion
- 6
- seat
- 100
- air current
- N
- radial direction phantom line
- M
- longitudinal direction phantom line
- A first aspect of the invention provides a fin-tube heat exchanger including a plurality of fins which have cut-and-raised parts and through which air current passes, and a plurality of heat transfer pipes which penetrate the plurality of fins and through which fluid flows, wherein the cut-and-raised parts are placed only on a downstream side of a center of the closest heat transfer pipe with respect to the air current, and the cut-and-raised parts incline with respect to the air current.
- According to this, the cut-and-raised part is provided only on the downstream side of the air current where frost is less prone to be formed, and it is possible to reduce the frost formation. Further, since water on the fin can be made to smoothly flow by the cut-and-raised part which inclines with respect to the air current direction, it is possible to enhance the drainage performance. Therefore, it is possible to enhance the heat transfer performance.
- According to a second aspect of the invention, especially in the first aspect, each of the fins includes a flat seat formed around the heat transfer pipe, a fin flat surface formed from the seat to a fin end located on the downstream side with respect to the air current, and a corrugated portion which is formed around the seat and around the fin flat surface and which have alternately formed peaks and valleys, and the cut-and-raised part is placed on the fin flat surface.
- According to this, since the corrugated portion is provided, a heat transfer area of the fin is increased. Further, water is induced by the fin flat surface formed from the seat around the heat transfer pipe to the fin end located on the downstream side of the air current, and it is possible to enhance the drainage performance.
- According to a third aspect of the invention, especially in the first or second aspect, the cut-and-raised part is formed into a bridge shape by a pair of raised sides connected to the fin and by a pair of cut-and-raised sides which are separated from the fin, a slit is formed between the cut-and-raised side and the fin, and the raised side is formed in a vertical direction.
- According to this, the raised side where water is prone to stay by surface tension is formed vertically, drainage water is made smoothly flow down and drainage performance is enhanced.
- According to a fourth aspect of the invention, especially in the third aspect, one of the raised sides of the cut-and-raised part located on an upstream side with respect to the air current is in a position higher than an other raised side located on the downstream side with respect to the air current.
- According to this, since precipitated water is guided toward the fin leeward end by its own weight and air current, drainage performance is enhanced.
- According to a fifth aspect of the invention, especially in the third aspect, one of the raised sides of the cut-and-raised part located on an upstream side with respect to the air current is in a position lower than an other raised side located on the downstream side with respect to the air current.
- According to this, since precipitated water is guided to a valley of the corrugated portion and is made to smoothly flow down, drainage performance is enhanced.
- According to a sixth aspect of the invention, especially in the first aspect, the cut-and-raised part is formed in a direction perpendicular to a straight line passing through the center of the closest heat transfer pipe.
- This configuration hinders heat transfer from a fin between the cut-and-raised part and the heat transfer pipe toward a fin downstream of the cut-and-raised part. Therefore, under an operating condition where frost is formed on the fin, it is possible to suppress frost formation on the fin located downstream of the cut-and-raised part in the air current direction.
- According to a seventh aspect of the invention, especially in the first aspect, the cut-and-raised part is formed parallel to a straight line passing through the center of the heat transfer pipe.
- According to this, since the cut-and-raised part is placed in parallel to a center axis of the heat transfer pipe, it is possible to maintain heat exchange performance without deteriorating heat transfer toward the leeward of the cut-and-raised part.
- According to an eighth aspect of the invention, especially in the second aspect, the fin includes a fin collar into which the heat transfer pipe is inserted, and the cut-and-raised part, the corrugated portion and the fin collar become larger in size in this order.
- According to this, it is possible to make it easy to laminate the fins.
- According to a ninth aspect of the invention, especially in any one of the first to eighth aspects, at least one of the fins located on an upstream side and one of the fins located on a downstream side are placed in a direction of the air current, and a height of the heat transfer pipe of the fin on the upstream side and a height of the heat transfer pipe of the fin on the downstream side are different from each other.
- According to this, since air current passing through the fin-tube heat exchanger can be guided to the entire fins, the fin-tube heat exchanger can substantially uniformly promote the heat transfer by the cut-and-raised part, and it is possible to uniform heat flux, to further promote the heat transfer, and to enhance the heat exchange ability.
- Embodiments of the present invention will be described below with reference to the drawings. The invention is not limited to the embodiments.
- Like the conventional fin-tube heat exchanger shown in
Figs. 18 , a fin-tube heat exchanger in a first embodiment of the present invention is composed of a plurality offins 1 arranged at predetermined intervals Fp from one another andheat transfer pipes 2 inserted into thefins 1 substantially at right angles. Here, the invention will be described based on a case where the fin-tube heat exchanger is used as an evaporator. -
Fig. 1(a) is a sectional view the fin configuring the fin-tube of the heat exchanger in the first embodiment, andFig. 1(b) is a partial plane view of the fin of the fin-tube heat exchanger. - As shown in
Fig. 1 , thefin 1 includes aflat seat 6, a finflat surface 1c and acorrugated portion 5. Generally, thecorrugated portion 5 is also called corrugate or waffle. - The
seat 6 is formed around aheat transfer pipe 2, and guides air current 100 to peripheries of afin collar 3. The finflat surface 1c is formed from theseat 6 to afin end 1d located downstream of the air current 100. Thecorrugated portion 5 is formed around theseat 6 and the finflat surface 1c, and peaks and valleys are alternately formed. - A cut-and-raised
part 4 is placed on the finflat surface 1c. The cut-and-raisedpart 4 is formed by offsetting a portion of thefin 1 from the finflat surface 1c in a slit form. - The cut-and-raised
part 4 is formed into a bridge shape by a pair of raisedsides 4b connected to the finflat surface 1c and by a pair of cut-and-raisedsides 4a separated from the finflat surface 1c. A cut-and-raised part opening (slit) 4c is formed between the cut-and-raisedsides 4a and the finflat surface 1c. - The raised sides 4b are formed in the vertical direction.
- The cut-and-raised
part 4 is placed only downstream of a center of the closestheat transfer pipe 2 in the direction of the air current 100, and the cut-and-raisedpart 4 inclines with respect to the air current 100. The raisedside 4b located upstream of the air current 100 is located at a position higher than the raisedside 4b located downstream of the air current 100. Of boundary lines between the finflat surface 1c and thecorrugated portion 5, a boundary line between the upper side and the lower side inclines in the same direction as the cut-and-raisedpart 4. - The cut-and-raised
part openings 4c are formed in an upper portion and a lower portion of the cut-and-raisedpart 4. Condensed drainage water flows down into the cut-and-raisedpart opening 4c and air current 100 passes through the cut-and-raisedpart opening 4c. Since the raisedside 4b is formed in the vertical direction, condensed drainage water easily flows down along the raisedside 4b by the gravity. - Centering on a phantom line L which connects centers of the
heat transfer pipes 2 to each other, if an upstream side of the air current 100 is defined as a fin windwardportion 1a and a downstream side of the air current 100 is defined as a finleeward portion 1b, the cut-and-raisedpart 4 is placed only on the fin leewardportion 1b. Thecorrugated portions 5 are placed on the fin windwardportion 1a and the fin leewardportion 1b. The cut-and-raisedpart 4 is placed on the finflat surface 1c located on an outer side of theseat 6. - As shown in
Fig. 2 , the cut-and-raisedpart 4 is formed in a direction (longitudinal direction) perpendicular to a radial direction phantom line N passing through a center of the closestheat transfer pipe 2. That is, the cut-and-raisedpart 4 is placed such that the straight cut-and-raisedside 4a intersects, at right angles, with the radial direction phantom line N of theheat transfer pipe 2 which is closest to the cut-and-raisedpart 4. - As shown in
Figs. 3 and4 , a height of thefin collar 3 is defined as Hc (e.g., 1.5 mm), a height of the cut-and-raisedpart 4 is defined as Hs (e.g., 0.75 mm) and a height of thecorrugated portion 5 is defined as Hw (e.g., 1mm). Here, these members are formed such that a relation Hc>Hw>Hs is satisfied. All of the cut-and-raisedparts 4 rise in the same direction with respect to the finflat surface 1c. - An operation of the fin-tube heat exchanger having the above-described configuration will be described below.
- In the fin-tube heat exchanger of this embodiment, at the fin windward
portion 1a formed on thecorrugated portion 5, since air current 100 passing through a gap of thefin 1 snakes, turbulence flow is promoted. At the fin leewardportion 1b, the air current 100 passes through the cut-and-raisedpart 4, and a temperature boundary layer is formed on the cut-and-raisedside 4a. - Generally, the cut-and-raised
part 4 promotes heat transfer. Therefore, if thecorrugated portion 5 and the cut-and-raisedpart 4 are placed, heat transfer of the fin leewardportion 1b having low thermal flow rate is promoted, and thermal flow rates of the fin windwardportion 1a and the fin leewardportion 1b become relatively uniform. - Especially, under an operating condition that temperature of the
fin 1 becomes lower than 0°C and frost is formed on the fin-tube heat exchanger, frost formation on the fin leewardportion 1b is promoted by the cut-and-raisedpart 4, and frost formation on the fin windwardportion 1a and frost formation on the fin leewardportion 1b become relatively uniform. - The cut-and-raised
part 4 is placed such that the cut-and-raisedside 4a (longitudinal direction phantom line M of cut-and-raised part 4) and the longitudinal direction phantom line N of theheat transfer pipe 2 which comes closest to this cut-and-raisedpart 4 intersect with each other at right angles. According to this, of the fin leewardportion 1b, heat transferred from thefin 1 between theheat transfer pipe 2 and the cut-and-raisedpart 4 to a region A of thefin 1 located downstream of the cut-and-raisedpart 4 in the direction of the air current 100 is shut off. Hence, under an operating condition that the temperature of thefin 1 becomes less than 0°C and frost is formed on the fin-tube heat exchanger, it is possible to restrain frost from being formed in the region A and even if the cut-and-raisedpart 4 is closed by the frost, the region A can be secured as an air trunk of the air current 100. - As shown in
Fig. 3 , the height Hw of thecorrugated portion 5 is set higher than the height Hs of the cut-and-raisedpart 4. According to this, air current 100 guided by thecorrugated portion 5 reliably passes through the cut-and-raisedpart 4 and heat transfer in the cut-and-raisedpart 4 can be promoted. - Since the cut-and-raised
part 4 is formed from the finflat surface 1c in the same direction as thefin collar 3, eddy of the air current 100 is not generated in the vicinity of the cut-and-raisedpart 4, and the air current 100 does not snake more than necessary. Hence, it is possible to restrain ventilation resistance caused by the cut-and-raisedpart 4 from increasing. - The cut-and-raised
part 4 opens upward and downward by the cut-and-raisedopening 4c and inclines such that upstream side of the cut-and-raisedpart 4 in the direction of the air current 100 becomes high. Hence, as shown inFig. 5 , drainage water which adheres to the cut-and-raisedpart 4 flows down by the air current 100 in addition to its own weight. Of drainage water which adheres to the cut-and-raisedpart 4, drainage water which flows down to the finflat surface 1c flows down by the air current 100 in addition to its own weight along the boundary line which inclines in the same direction as that of the cut-and-raisedpart 4. - Therefore, the drainage water smoothly flows down against surface tension of the
fin 1 which tries to stay the drainage water, and to reduce an amount of water staying on thefin 1. According to this, even under an operating condition that drainage water adheres to thefin 1, it is possible to enhance the drainage performance of drainage water and to reduce the ventilation resistance of the fin-tube heat exchanger. - Under an operating condition that the temperature of the
fin 1 becomes less than 0°C and frost is formed on the fin-tube heat exchanger, at the time of defrosting, melted water produced when frost is melted smoothly flows down utilizing the inclination of the cut-and-raisedpart 4. Therefore, at the time of returning, it is possible to avoid a case where melted water staying on thefin 1 is again frozen and ventilation resistance is increased. - Further, by setting the height Hc of the
fin collar 3 higher than the height Hs of the cut-and-raisedpart 4 as shown inFig. 4 , the adjacent finflat surface 1c and cut-and-raisedpart 4 do not come into contact with each other, and the amount of drainage water staying due to the surface tension of thefin 1 can be reduced. - According to this, even under an operating condition that drainage water adheres to the
fin 1, it is possible to enhance the drainage performance of drainage water, and to reduce the ventilation resistance of the fin-tube heat exchanger. - Further, since the cut-and-raised
part 4 is placed on an outer side of theseat 6, it is possible to secure a predetermined interval between the cut-and-raisedpart 4 and thefin collar 3. Hence, drainage water which adheres to the cut-and-raisedpart 4 does not stay between the cut-and-raisedpart 4 and thefin collar 3 by the surface tension, and flows downward. Therefore, even under the operating condition that drainage water adheres to thefin 1, it is possible to enhance the drainage performance of drainage water and to reduce the ventilation resistance of the fin-tube heat exchanger. - When the
seat 6 and the finflat surface 1c are formed on the same plane, a length formed between contact points 20 of thecorrugated portion 5 and theseat 6 is defined as a distance D, a circular region having the distance D as a diameter is defined as theseat 6, and outside of theseat 6 is defined as the finflat surface 1c. - As described above, in this embodiment, the cut-and-raised
part 4 which inclines with respect to the air current 100 is provided on the fin leewardportion 1b, and heat transfer of the fin leewardportion 1b is promoted. Hence, under the operating condition that the temperature of thefin 1 becomes less than 0°C, frost is formed on the fin windwardportion 1a and the fin leewardportion 1b relatively uniformly and in addition, melted water produced at the time of defrosting is less prone to stay on thefin 1. - Hence, it is possible to avoid a case where frost is locally formed on the cut-and-raised
part 4 and ventilation resistance abruptly increases, reduction in a heat exchanging amount is suppressed, and heat transfer is promoted by the cut-and-raisedpart 4. Further, it is possible to largely improve frost formation on the conventional fin-tube heat exchanger. - Although the cut-and-raised
part 4 and thefin collar 3 are provided in the same direction in this embodiment, the cut-and-raisedpart 4 may be formed in a direction different from thefin collar 3. -
Figs. 6 show a second embodiment of the invention. The same symbols are allocated to configurations having the same functions as those of the first embodiment, description thereof will be omitted, and only configurations which are different from the first embodiment will be described below. - Some of cut-and-raised
parts 4 are formed by offsetting a portion of afin 1 shown inFig. 1 in a slit form. In addition, the cut-and-raisedparts 4 may be formed by bending a portion of afin 1 shown inFigs. 6(a) and 6(b) substantially perpendicularly to a finflat surface 1c. - In the second embodiment, one side is a raised
side 4b, and other three sides are cut-and-raisedsides 4a which are separated from a finflat surface 1c. By bending the portion of thefin 1 by the raisedside 4b, a cut-and-raisedopening 4c is formed. -
Figs. 7 show a third embodiment of the invention. The same symbols are allocated to configurations having the same functions as those of the first embodiment, description thereof will be omitted, and only configurations which are different from the first embodiment will be described below. - As shown in
Figs. 7(a) and 7(b) , a cut-and-raisedpart 4 inclines such that a downstream side thereof in the direction of air current 100 is located at a high position. - That is, in the cut-and-raised
part 4, the raisedside 4b located on the upstream side of the air current 100 is located at a position lower than a raisedside 4b located on the downstream side of air current 100. Of the boundary lines between a finflat surface 1c and acorrugated portion 5, a boundary line between the upper side and the lower side inclines in the same direction as the cut-and-raisedpart 4. - According to this configuration, at the time of defrosting, melted water produced when frost is melted smoothly flows down utilizing the inclination of the cut-and-raised
part 4. Of drainage water which adheres to the cut-and-raisedpart 4, drainage water which flows down to the finflat surface 1c flows down along the boundary line which inclines in the same direction as the cut-and-raisedpart 4. By peaks and valleys formed by thecorrugated portions 5, melted water flows downward in the gravity direction. Hence, it is possible to reduce the amount of water staying at afin 1, and to avoid a case where melted water after defrosting and returning is again frozen to increase the ventilation resistance. - By forming the
corrugated portions 5 on the upstream side and the downstream side of the air current 100, a temperature boundary layer in the surface of thefin 1 is disturbed and heat transfer is promoted. Therefore, the frost formation is reduced, drainage performance is maintained, and heat exchanging ability can be enhanced. - Although it is described in the embodiment that the
heat transfer pipe 2 is a round pipe, theheat transfer pipe 2 may be a flat pipe for example. - Further, the cut-and-raised
part 4 described in the second embodiment may be applied to the third embodiment. -
Fig. 8 is a partial plane view of a fin configuring a fin-tube heat exchanger in a fourth embodiment of the invention. The same symbols are allocated to the same members as those of the first to third embodiments, and detailed description thereof will be omitted, - As shown in
Fig. 8 , in the fin-tube heat exchanger in the fourth embodiment, a plurality offins 1 are arranged in parallel to a direction of air current 100. That is, in the fin-tube heat exchanger in the fourth embodiment, at least afin 1 in a first row located on the upstream side and thefin 1 in a second row located on the downstream side are placed. - A height of a
heat transfer pipe 2 of thefin 1 in the first row on the upstream side and a height of theheat transfer pipe 2 of thefin 1 in the second row on the downstream side are different from each other. It is preferable that theheat transfer pipe 2 of thefin 1 in the second row is placed between the twoheat transfer pipes 2 of thefin 1 in the first row. - According to the fin-tube heat exchanger of the fourth embodiment, the air current 100 which passes through the
fin 1 in the first row easily exchanges heat with theheat transfer pipe 2 of thefin 1 in the second row. - The air current 100 passes through any one of cut-and-raised
parts 4 provided in thefin 1 in the first row and thefin 1 in the second row. Therefore, a temperature boundary layer is formed in the air current 100 by the cut-and-raisedpart 4 in the first row and the second row relatively uniformly, and heat transfer can be promoted. - As described above, in the fourth embodiment, the fin leeward
portion 1b is provided with the cut-and-raisedpart 4 which inclines with respect to the air current 100, thefins 1 are arranged in two rows in the direction of the air current 100, and the height of theheat transfer pipe 2 of thefin 1 in the first row and the height of theheat transfer pipe 2 of thefin 1 in the second row on the downstream side are different from each other. - According to this, heat transfer of the air current 100 passing through any of the positions of the fin-tube heat exchanger is promoted by the cut-and-raised
part 4 relatively uniformly, and heat exchange ability can be enhanced. - Under the operating condition that the surface temperature of the
fin 1 becomes less than 0°C, frost is formed on the fin windwardportion 1a and the fin leewardportion 1b relatively uniformly, and at the time of defrosting, it is possible to prevent melted water from being again frozen, and it is possible to remarkably improve the frost formation on the fin-tube heat exchanger having the conventional cut-and-raisedparts 4. - A fifth embodiment of the invention will be described with reference to the drawing.
- Like the conventional fin-tube heat exchanger shown in
Figs. 18 , a fin-tube heat exchanger in the fifth embodiment of the invention is composed of a plurality offins 1 arranged at predetermined intervals Fp from one another, andheat transfer pipes 2 inserted into thefins 1 substantially at right angles. The fifth embodiment will be described based on an example in which the fin-tube heat exchanger is used as an evaporator. -
Fig. 9 (a) is a sectional view of the fin configuring the fin-tube heat exchanger in the fifth embodiment, andFig. 9(b) is a partial plane view of the fin of the fin-tube heat exchanger. - As shown in
Fig. 9 , thefin 1 includesflat seats 6, finflat surfaces 1c andcorrugated portions 5. Generally, thecorrugated portion 5 is also called corrugate or waffle. - The
seat 6 is formed around theheat transfer pipe 2, and guides air current 100 to peripheries of afin collar 3. The finflat surface 1c is formed from theseat 6 to afin end 1d located downstream of the air current 100. Thecorrugated portion 5 is formed around theseat 6 and the finflat surface 1c, and peaks and valleys are alternately formed. - A cut-and-raised
part 4 is placed on the finflat surface 1c. The cut-and-raisedpart 4 is formed by offsetting a portion of the finflat surface 1c from the finflat surface 1c in a slit form. - The cut-and-raised
part 4 is formed into a bridge shape by a pair of raisedsides 4b connected to the finflat surface 1c and by a pair of cut-and-raisedsides 4a separated from the finflat surface 1c. A cut-and-raised part opening (slit) 4c is formed between the cut-and-raisedsides 4a and the finflat surface 1c. - The raised sides 4b are formed in the vertical direction.
- The cut-and-raised
part 4 is placed only downstream of a center of the closestheat transfer pipe 2 in the direction of the air current 100, and the cut-and-raisedpart 4 inclines with respect to the air current 100. The raisedside 4b located upstream of the air current 100 is located at a position higher than the raisedside 4b located downstream of the air current 100. Of boundary lines between the finflat surface 1c and thecorrugated portion 5, a boundary line between the upper side and the lower side inclines in the same direction as the cut-and-raisedpart 4. - The cut-and-raised
part 4 is parallel to a radial direction phantom line N passing through a center of theheat transfer pipe 2. - The two cut-and-raised
parts 4 of the fifth embodiment are placed on both sides of the radial direction phantom line N passing through the center of theheat transfer pipe 2 such that the upstream side of the air current 100 comes on the upper side. - The cut-and-raised
part openings 4c are formed in an upper portion and a lower portion of the cut-and-raisedpart 4. Condensed drainage water flows down into the cut-and-raisedpart opening 4c and air current 100 passes through the cut-and-raisedpart opening 4c. Since the raisedside 4b is formed in the vertical direction, condensed drainage water easily flows down along the raisedside 4b by the gravity. - Centering on a phantom line L which connects centers of the
heat transfer pipes 2 to each other, if an upstream side of the air current 100 is defined as a fin windwardportion 1a and a downstream side of the air current 100 is defined as a finleeward portion 1b, the cut-and-raisedpart 4 is placed only on the fin leewardportion 1b. Thecorrugated portions 5 are placed on the fin windwardportion 1a and the fin leewardportion 1b. The cut-and-raisedpart 4 is placed on the finflat surface 1c located on an outer side of theseat 6 which is formed into a circular shape around thefin collar 3. - As shown in
Figs. 11 and12 , a height of thefin collar 3 is defined as Hc (e.g., 1.5 mm), a height of the cut-and-raisedpart 4 is defined as Hs (e.g., 0.75 mm) and a height of thecorrugated portion 5 is defined as Hw (e.g., 1 mm). Here, these members are formed such that a relation Hc>Hw>Hs is satisfied. All of the cut-and-raisedparts 4 rise in the same direction with respect to the finflat surface 1c. - An operation of the fin-tube heat exchanger having the above-described configuration will be described below.
- In the fin-tube heat exchanger of this embodiment, at the fin windward
portion 1a formed on thecorrugated portion 5, since air current 100 passing through a gap of thefin 1 snakes, turbulence flow is promoted. At the fin leewardportion 1b, the air current 100 passes through the cut-and-raisedpart 4, and a temperature boundary layer is formed on the cut-and-raisedside 4a. - Generally, the cut-and-raised
part 4 promotes heat transfer. Therefore, if thecorrugated portion 5 and the cut-and-raisedpart 4 are placed, heat transfer of the fin leewardportion 1b having low thermal flow rate is promoted, and thermal flow rates of the fin windwardportion 1a and the fin leewardportion 1b become relatively uniform. - Especially, under an operating condition that temperature of the
fin 1 becomes lower than 0°C and frost is formed on the fin-tube heat exchanger, frost formation on the fin leewardportion 1b is promoted by the cut-and-raisedpart 4, and frost formation on the fin windwardportion 1a and frost formation on the fin leewardportion 1b become relatively uniform. - The cut-and-raised
part 4 is placed substantially parallel to the radial direction phantom line N of theheat transfer pipe 2. Normally, heat is transferred between theheat transfer pipe 2 and thefin 1 such that isotherms T0, T1, T2, T3, T4 ... radially spread from a center of theheat transfer pipe 2 as shown inFig. 10 . Hence, the cut-and-raisedpart 4 and the isotherms which spread from theheat transfer pipe 2 intersect with each other substantially perpendicularly. - That is, heat moves in a direction perpendicular to the isotherm as shown by broken arrows in
Fig. 10 . Hence, although the cut-and-raisedpart 4 placed substantially parallel to the radial direction phantom line N forms a discontinuous surface on thefin 1, heat transfer between thefin 1 and theheat transfer pipe 2 is not blocked, and the cut-and-raisedpart 4 does not act as heat resistance between thefin 1 and theheat transfer pipe 2. - The cut-and-raised
part 4 which is placed substantially parallel to the radial direction phantom line N of theheat transfer pipe 2 promotes heat transfer between theheat transfer pipe 2 and an end of thefin 1 having a great distance from theheat transfer pipe 2. According to this, a thermal flow rate in the vicinity of theheat transfer pipe 2 and a thermal flow rate around the end of thefin 1 become relatively uniform. - As shown in
Fig. 11 , the height Hw of thecorrugated portion 5 is made higher than the height Hs of the cut-and-raisedpart 4. According to this, the air current 100 which is guided by thecorrugated portion 5 more reliably passes through the cut-and-raisedpart 4, and it is possible to promote the heat transfer by the cut-and-raisedpart 4. - Since the cut-and-raised
part 4 is formed from the finflat surface 1c in the same direction as thefin collar 3, eddy of the air current 100 is not generated in the vicinity of the cut-and-raisedpart 4, and the air current 100 does not snake more than necessary. Hence, it is possible to restrain ventilation resistance caused by the cut-and-raisedpart 4 from increasing. - The cut-and-raised
part 4 opens upward and downward by the cut-and-raisedopening 4c and inclines such that upstream side of the cut-and-raisedpart 4 in the direction of the air current 100 becomes high. Hence, as shown inFig. 13 , drainage water which adheres to the cut-and-raisedpart 4 flows down by the air current 100 in addition to its own weight. Of drainage water which adheres to the cut-and-raisedpart 4, drainage water which flows down to the finflat surface 1c flows down by the air current 100 in addition to its own weight along the boundary line which inclines in the same direction as that of the cut-and-raisedpart 4. - Therefore, the drainage water smoothly flows down against surface tension of the
fin 1 which tries to stay the drainage water, and to reduce an amount of water staying on thefin 1. According to this, even under an operating condition that drainage water adheres to thefin 1, it is possible to enhance the drainage performance of drainage water and to reduce the ventilation resistance of the fin-tube heat exchanger. - Under an operating condition that the temperature of the
fin 1 becomes less than 0°C and frost is formed on the fin-tube heat exchanger, at the time of defrosting, melted water produced when frost is melted smoothly flows down utilizing the inclination of the cut-and-raisedpart 4. Therefore, at the time of defrosting and returning, it is possible to avoid a case where melted water staying on thefin 1 is again frozen and ventilation resistance is increased. - Further, by setting the height Hc of the
fin collar 3 higher than the height Hs of the cut-and-raisedpart 4 as shown inFig. 12 , the adjacent finflat surface 1c and cut-and-raisedpart 4 do not come into contact with each other, and the amount of drainage water staying between thelaminated fins 1 due to the surface tension of thefin 1 can be reduced. - According to this, even under an operating condition that drainage water adheres to the
fin 1, it is possible to enhance the drainage performance of drainage water, and to reduce the ventilation resistance of the fin-tube heat exchanger. - Further, since the cut-and-raised
part 4 is placed on an outer side of thecircular seat 6 which is formed around thefin collar 3, it is possible to secure a predetermined interval between the cut-and-raisedpart 4 and thefin collar 3. Hence, drainage water which adheres to the cut-and-raisedpart 4 does not stay between the cut-and-raisedpart 4 and thefin collar 3 by the surface tension, and flows downward. Therefore, even under the operating condition that drainage water adheres to thefin 1, it is possible to enhance the drainage performance of drainage water and to reduce the ventilation resistance of the fin-tube heat exchanger. - When the
seat 6 and the finflat surface 1c are formed on the same plane, a length formed between contact points 20 of thecorrugated portion 5 and theseat 6 is defined as a distance D, a circular region having the distance D as a diameter is defined as theseat 6, and outside of theseat 6 is defined as the finflat surface 1c. - As described above, in this embodiment, the cut-and-raised
part 4 which inclines with respect to the air current 100 is provided on the fin leewardportion 1b, and heat transfer of the fin leewardportion 1b is promoted. Hence, under the operating condition that the temperature of thefin 1 becomes less than 0°C, frost is formed on the fin windwardportion 1a and the fin leewardportion 1b relatively uniformly and in addition, melted water produced at the time of defrosting is less prone to stay on thefin 1. - Hence, it is possible to avoid a case where frost is locally formed on the cut-and-raised
part 4 and ventilation resistance abruptly increases, reduction in a heat exchanging amount is suppressed, and heat transfer is promoted by the cut-and-raisedpart 4. Further, it is possible to largely improve frost formation on the conventional fin-tube heat exchanger. - Although the cut-and-raised
part 4 and thefin collar 3 are provided in the same direction in this embodiment, the cut-and-raisedpart 4 may be formed in a direction different from thefin collar 3. -
Figs. 14 show a sixth embodiment of the invention. The same symbols are allocated to configurations having the same functions as those of the fifth embodiment, description thereof will be omitted, and only configurations which are different from the fifth embodiment will be described below. - Some of cut-and-raised
parts 4 are formed by offsetting a portion of afin 1 shown inFig. 9 in a slit form. In addition, the cut-and-raisedparts 4 may be formed by bending a portion of afin 1 shown inFigs. 14(a) and 14(b) substantially perpendicularly to a finflat surface 1c. - In the sixth embodiment, one side is a raised
side 4b, and other three sides are cut-and-raisedsides 4a which are separated from a finflat surface 1c. By bending the portion of thefin 1 by the raisedside 4b, a cut-and-raisedopening 4c is formed. -
Figs. 15 show a seventh embodiment of the invention. The same symbols are allocated to configurations having the same functions as those of the fifth embodiment, description thereof will be omitted, and only configurations which are different from the fifth embodiment will be described below. - As shown in
Figs. 15 (a) and 15 (b) , a cut-and-raisedpart 4 inclines such that a downstream side thereof in the direction of air current 100 is located at a high position. - That is, in the cut-and-raised
part 4, the raisedside 4b located on the upstream side of the air current 100 is located at a position lower than a raisedside 4b located on the downstream side of air current 100. Of the boundary lines between a finflat surface 1c and acorrugated portion 5, a boundary line between the upper side and the lower side inclines in the same direction as the cut-and-raisedpart 4. - According to this configuration, at the time of defrosting, melted water produced when frost is melted smoothly flows down utilizing the inclination of the cut-and-raised
part 4. Of drainage water which adheres to the cut-and-raisedpart 4, drainage water which flows down to the finflat surface 1c flows down along the boundary line which inclines in the same direction as the cut-and-raisedpart 4. By peaks and valleys formed by thecorrugated portions 5, melted water flows downward in the gravity direction. Hence, it is possible to reduce the amount of water staying at afin 1, and to avoid a case where melted water after defrosting and returning is again frozen to increase the ventilation resistance. - By forming the
corrugated portions 5 on the upstream side and the downstream side of the air current 100, a temperature boundary layer in the surface of thefin 1 is disturbed and heat transfer is promoted. Therefore, the frost formation is reduced, drainage performance is maintained, and heat exchanging ability can be enhanced. - Although it is described in the embodiment that the
heat transfer pipe 2 is a round pipe, theheat transfer pipe 2 may be a flat pipe for example. - Further, the cut-and-raised
part 4 described in the sixth embodiment may be applied to the seventh embodiment. -
Fig. 16 is a partial plane view of a fin configuring a fin-tube heat exchanger in an eighth embodiment of the invention. The same symbols are allocated to the same members as those of the first to seventh embodiments, and detailed description thereof will be omitted, - As shown in
Fig. 16 , in the fin-tube heat exchanger in the eighth embodiment, a plurality offins 1 are arranged in parallel to a direction of air current 100. That is, in the fin-tube heat exchanger in the eighth embodiment, at least afin 1 in a first row located on the upstream side and thefin 1 in a second row located on the downstream side are placed. - A height of a
heat transfer pipe 2 of thefin 1 in the first row on the upstream side and a height of theheat transfer pipe 2 of thefin 1 in the second row on the downstream side are different from each other. It is preferable that theheat transfer pipe 2 of thefin 1 in the second row is placed between the twoheat transfer pipes 2 of thefin 1 in the first row. - According to the fin-tube heat exchanger of this embodiment, the air current 100 which passes through the
fin 1 in the first row easily exchanges heat with theheat transfer pipe 2 of thefin 1 in the second row. - The air current 100 passes through any one of cut-and-raised
parts 4 provided in thefin 1 in the first row and thefin 1 in the second row. Therefore, a temperature boundary layer is formed by the cut-and-raisedpart 4, and heat transfer can be promoted. - As described above, in the this embodiment, the fin leeward
portion 1b is provided with the cut-and-raisedpart 4 which inclines with respect to the air current 100, thefins 1 are arranged in two rows in the direction of the air current 100, and the height of theheat transfer pipe 2 of thefin 1 in the first row and the height of theheat transfer pipe 2 of thefin 1 in the second row on the downstream side are different from each other. - According to this, heat transfer of the air current 100 passing through any of the positions of the fin-tube heat exchanger is promoted by the cut-and-raised
part 4, and heat exchange ability can be enhanced. - Under the operating condition that the surface temperature of the
fin 1 becomes less than 0°C, frost is formed on the fin windwardportion 1a and the fin leewardportion 1b relatively uniformly, and at the time of defrosting, it is possible to prevent melted water from being again frozen, and it is possible to remarkably improve the frost formation on the fin-tube heat exchanger having the conventional cut-and-raisedparts 4. - As described above, the fin-tube heat exchanger of the present invention is formed only on the downstream side of the fin with respect to the direction of air current, frost formation can be reduced by the cut-and-raised part which inclines with respect to the direction of the air current, and drainage performance can be enhanced. Therefore, the invention can be applied to a heat exchanger of a refrigeration cycle device used for an air conditioner, a water heater and a heating system.
Claims (9)
- A fin-tube heat exchanger comprising
a plurality of fins (1) which have cut-and-raised parts (4) and through which air current passes, and
a plurality of heat transfer pipes (2) which penetrate the plurality of fins (1) and through which fluid flows, wherein
each of the fins (1) includes a flat seat (6) formed around the heat transfer pipe (2); a fin flat surface (1c) formed from the seat (6) to a fin end (1d) located on downstream side with respect to the air current, and a corrugated portion (5) which has alternately formed peaks and valleys,
the cut-and-raised parts (4) are placed only on the fin flat surface (1c) of the downstream side of a center of the closest heat transfer pipe with respect to the air current,
characterised in that said corrugated portion (5) is formed around the seat and around the fin flat surface, said cut-and-raised parts (4) incline with respect to the air current, and
the fin-tube heat exchange comprises of boundary lines between the fin flat surface (1c) on which the cut-and raised part (4) is placed and the corrugated portion (5), wherein a boundary line of a lower side of the cut-and raised part inclines in the same direction as the cut-and raised part. - The fin-tube heat exchanger according to claim 1, wherein the cut-and-raised part is formed into a bridge shape by a pair of raised sides connected to the fin and by a pair of cut-and-raised sides which are separated from the fin,
a slit is formed between the cut-and-raised side and the fin, and
the raised side is formed in a vertical direction. - The fin-tube heat exchanger according to claim 2, wherein one of the raised sides of the cut-and-raised part located on an upstream side with respect to the air current is in a position higher than an other raised side located on the downstream side with respect to the air current.
- The fin-tube heat exchanger according to claim 2, wherein one of the raised sides of the cut-and-raised part located on an upstream side with respect to the air current is in a position lower than an other raised side located on the downstream side with respect to the air current.
- The fin-tube heat exchanger according to claim 1, wherein the cut-and-raised part is formed in a direction perpendicular to a straight line passing through the center of the closest heat transfer pipe.
- The fin-tube heat exchanger according to claim 1, wherein the cut-and-raised part is formed parallel to a straight line passing through the center of the heat transfer pipe.
- The fin-tube heat exchanger according to claim 1, wherein the fin includes a fin collar into which the heat transfer pipe is inserted, and
the cut-and-raised part, the corrugated portion and the fin collar become larger in size in this order. - The fin-tube heat exchanger according to any one of claims 1 to 7, wherein at least one of the fins located on an upstream side and one of the fins located on a downstream side are placed in a direction of the air current, and
a height of the heat transfer pipe of the fin on the upstream side and a height of the heat transfer pipe of the fin on the downstream side are different from each other. - A refrigeration cycle device comprising the fin-tube
heat exchanger according to any one of claims 1 to 8.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012102211 | 2012-04-27 | ||
JP2012105714 | 2012-05-07 | ||
JP2012250915 | 2012-11-15 | ||
JP2012250916 | 2012-11-15 | ||
PCT/JP2013/002312 WO2013161193A1 (en) | 2012-04-27 | 2013-04-03 | Fin-tube heat exchanger and refrigeration cycle device using same |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2843345A1 EP2843345A1 (en) | 2015-03-04 |
EP2843345A4 EP2843345A4 (en) | 2015-06-24 |
EP2843345B1 true EP2843345B1 (en) | 2017-01-11 |
Family
ID=49482548
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13781555.1A Active EP2843345B1 (en) | 2012-04-27 | 2013-04-03 | Fin-tube heat exchanger and refrigeration cycle device using same |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2843345B1 (en) |
JP (1) | JP6021081B2 (en) |
CN (1) | CN104272053B (en) |
WO (1) | WO2013161193A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11199344B2 (en) * | 2015-07-10 | 2021-12-14 | Mitsubishi Electric Corporation | Heat exchanger and air-conditioning apparatus |
JP2020016418A (en) * | 2018-07-27 | 2020-01-30 | 株式会社ノーリツ | Heat exchanger, and water heating system including the same |
CN109186307B (en) * | 2018-09-30 | 2020-01-17 | 珠海格力电器股份有限公司 | Fin and heat exchanger with same |
CN110425904A (en) * | 2019-08-13 | 2019-11-08 | 青岛海信日立空调系统有限公司 | A kind of plate fin and micro-channel heat exchanger, air-conditioning |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5552228Y2 (en) * | 1975-04-28 | 1980-12-04 | ||
US4705105A (en) * | 1986-05-06 | 1987-11-10 | Whirlpool Corporation | Locally inverted fin for an air conditioner |
JPH06300474A (en) * | 1993-04-12 | 1994-10-28 | Daikin Ind Ltd | Heat exchanger with fin |
JPH08296988A (en) * | 1995-04-25 | 1996-11-12 | Daikin Ind Ltd | Cross-fin heat exchanger |
KR0133026Y1 (en) * | 1995-07-13 | 1999-01-15 | 김광호 | Heat exchanger fin |
JPH09189492A (en) * | 1996-01-10 | 1997-07-22 | Hitachi Ltd | Heat transfer fin |
JPH109786A (en) * | 1996-06-21 | 1998-01-16 | Matsushita Refrig Co Ltd | Finned heat exchanger |
JPH10339595A (en) * | 1997-06-10 | 1998-12-22 | Mitsubishi Heavy Ind Ltd | Heat exchanger |
JP3211728B2 (en) * | 1997-06-23 | 2001-09-25 | ダイキン工業株式会社 | Cross fin heat exchanger |
JPH11118379A (en) * | 1997-10-15 | 1999-04-30 | Sanden Corp | Multi-tube heat exchanger |
JP2001091101A (en) * | 1999-09-20 | 2001-04-06 | Fujitsu General Ltd | Heat exchanger for air conditioner |
KR100932677B1 (en) * | 2001-08-10 | 2009-12-22 | 요코하마 티엘오 가부시키가이샤 | Heat transfer device |
JP2006138504A (en) * | 2004-11-10 | 2006-06-01 | Mitsubishi Heavy Ind Ltd | Heat exchanger and air conditioner |
JP4626422B2 (en) * | 2005-07-01 | 2011-02-09 | ダイキン工業株式会社 | Finned tube heat exchanger |
JP2007309533A (en) | 2006-05-16 | 2007-11-29 | Matsushita Electric Ind Co Ltd | Fin tube heat exchanger |
JP4940871B2 (en) | 2006-10-02 | 2012-05-30 | ダイキン工業株式会社 | Finned tube heat exchanger |
KR20110083017A (en) * | 2010-01-13 | 2011-07-20 | 엘지전자 주식회사 | Fin for heat exchanger and heat exchanger having the same |
-
2013
- 2013-04-03 CN CN201380022277.8A patent/CN104272053B/en active Active
- 2013-04-03 EP EP13781555.1A patent/EP2843345B1/en active Active
- 2013-04-03 JP JP2014512319A patent/JP6021081B2/en active Active
- 2013-04-03 WO PCT/JP2013/002312 patent/WO2013161193A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
CN104272053A (en) | 2015-01-07 |
JPWO2013161193A1 (en) | 2015-12-21 |
CN104272053B (en) | 2016-10-12 |
JP6021081B2 (en) | 2016-11-02 |
WO2013161193A1 (en) | 2013-10-31 |
EP2843345A4 (en) | 2015-06-24 |
EP2843345A1 (en) | 2015-03-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8613307B2 (en) | Finned tube heat exchanger | |
CN101441047B (en) | Heat exchanger of plate fin and tube type | |
JP2006322698A (en) | Heat exchanger | |
EP2843345B1 (en) | Fin-tube heat exchanger and refrigeration cycle device using same | |
US20100175864A1 (en) | Fin tube heat exchanger | |
KR20110055839A (en) | Heat exchanger and air conditioner having the same | |
EP2314973B1 (en) | Fin-tube heat exchanger | |
JP2011202855A (en) | Refrigerator | |
JP4775429B2 (en) | Finned tube heat exchanger | |
JP2008025897A (en) | Outdoor unit heat exchanger for heating, ventilating, air conditioning system | |
JP5009413B2 (en) | Heat exchanger and air conditioner equipped with the same | |
JP4073850B2 (en) | Heat exchanger | |
JP2014089018A (en) | Fin tube heat exchanger and refrigeration cycle device including the same | |
JP2009204277A (en) | Heat exchanger | |
EP3608618B1 (en) | Heat exchanger and refrigeration cycle device | |
JP6706839B2 (en) | Fin tube heat exchanger | |
JP2007017042A (en) | Heat exchanger | |
EP3550247B1 (en) | Heat exchanger and air conditioner | |
JP2010025482A (en) | Heat exchanger | |
CN107860248A (en) | A kind of micro-channel heat exchanger and air-conditioning | |
JP2001141383A (en) | Heat exchanger | |
JP2008249298A (en) | Fin tube type heat exchanger | |
JP2014089019A (en) | Fin tube heat exchanger and refrigeration cycle device including the same | |
JP2008275303A (en) | Heat exchanger | |
JP6131460B2 (en) | Finned heat exchanger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20141127 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
RA4 | Supplementary search report drawn up and despatched (corrected) |
Effective date: 20150528 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F25B 39/02 20060101ALI20150521BHEP Ipc: F28F 1/32 20060101AFI20150521BHEP |
|
DAX | Request for extension of the european patent (deleted) | ||
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20160324 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAJ | Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted |
Free format text: ORIGINAL CODE: EPIDOSDIGR1 |
|
GRAL | Information related to payment of fee for publishing/printing deleted |
Free format text: ORIGINAL CODE: EPIDOSDIGR3 |
|
INTC | Intention to grant announced (deleted) | ||
GRAR | Information related to intention to grant a patent recorded |
Free format text: ORIGINAL CODE: EPIDOSNIGR71 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
INTG | Intention to grant announced |
Effective date: 20161201 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 861690 Country of ref document: AT Kind code of ref document: T Effective date: 20170115 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602013016517 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 5 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20170111 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 861690 Country of ref document: AT Kind code of ref document: T Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170411 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170412 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170511 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170511 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170411 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602013016517 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
26N | No opposition filed |
Effective date: 20171012 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170411 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170430 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170430 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170403 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170411 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20170430 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 6 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170403 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170403 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20130403 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20230424 Year of fee payment: 11 Ref country code: DE Payment date: 20230420 Year of fee payment: 11 |