EP3015808B1 - Heat exchanger, heat exchanger structure, and fin for heat exchanger - Google Patents
Heat exchanger, heat exchanger structure, and fin for heat exchanger Download PDFInfo
- Publication number
- EP3015808B1 EP3015808B1 EP13888478.8A EP13888478A EP3015808B1 EP 3015808 B1 EP3015808 B1 EP 3015808B1 EP 13888478 A EP13888478 A EP 13888478A EP 3015808 B1 EP3015808 B1 EP 3015808B1
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- EP
- European Patent Office
- Prior art keywords
- heat transfer
- fin
- tubes
- heat exchanger
- heat
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
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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
- F28F1/126—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 consisting of zig-zag shaped fins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
Definitions
- one heat exchanger functions as a condenser during a cooling operation and as an evaporator during a heating operation.
- a heat exchanger in an outdoor unit functions as an evaporator during the heating operation.
- the evaporator performs the heating operation during cold weather, for example, when the outside air temperature is as low as about -5°C, a frosting phenomenon occurs in the evaporator in which moisture in the air attaches to the evaporator as frost.
- frosting occurs from the upwind side of the heat exchanger, and the frost gradually grows toward the downwind side.
- a fin heat transfer area for directly exchanging heat with the air is reduced, thereby reducing a heating capability.
- the frosting narrows a ventilation path between fins to reduce the volume of air, which also reduces the heating capability.
- the heat exchanger of the present invention includes the heat transfer walls including a first edge portion and a second edge portion indented toward the downwind side relative to the first edge portion, and the first edge portion and the second edge portion are each disposed at least on every other layer in the direction of the arrangement. Accordingly, a fin pitch between the first edge portions adjacent to each other in the arrangement direction can be widened. As a result, even if frosting occurs locally on the first edge portions positioned on an upwind side end of the fin, the heat exchanger can exchange heat continuously on the downwind side because the ventilation path is secured.
- the drainage of the melt water can be improved also on the downwind side. Further, even if the remaining melt water solidifies, a heat transfer area of the fin available for exchanging heat directly with the air can be secured appropriately, and in addition, the ventilation path can be prevented from becoming easily clogged.
- the tubes 21 each have a flat cross section and include a flowpath for a refrigerant penetrating therethrough in the axial direction.
- the tubes 21 are manufactured by extruding copper or a copper alloy, or aluminum or an aluminum alloy that have excellent thermal conductivity, or by roll forming a plate-like material.
- the header tubes 30 may be manufactured from a material similar to that of the tubes 21.
- the tubes 21 may be manufactured integrally or may be manufactured by combining several members.
- an air conditioner including the heat exchanger 10 as an outdoor heat exchanger is performing the heating operation in a low outside air temperature, frosting occurs on the fin 22 on the upwind side of the airflow A.
- the upwind side of the airflow A may simply be referred to as the upwind side for short.
- the air conditioner performs a defrosting operation, for example, regularly for removing the attached frost. If the melt water remains not being fully drained from the heat exchanger 10 after the defrosting operation, it might freeze after resumption of the heating operation, possibly causing frosting again.
- a second condition is that the heat transfer pieces 23L and 23R are each disposed on every other layer of the heat transfer wall 23, such that the heat transfer pieces 23L and 23R appear alternately on the opposite sides of the midpoint M in the width direction X.
- the condition is equivalent to that the cutouts are disposed on every other layer of the heat transfer wall 23, alternately on the opposite sides of the midpoint M in the width direction X.
- the fin 22 can minimize a reduction in heat exchange efficiency.
- the heat exchanger 10 can ensure a desired heat transfer performance within the area U if the heat transfer pieces 23L and 23R are connected to the tubes 21 such that the heat transfer pieces 23L and 23R are able to exchange heat with the tubes 21.
- the cutouts of the fin 22 of the embodiment each have a rectangular shape as seen in a plan view
- the cutouts may have any shape as long as the embodiment achieves the objects of the present invention.
- the cutouts may adopt several shapes including a circular cutout ( FIG. 6A ), a triangular cutout ( FIG. 6B ), a polygonal cutout ( FIG. 6C ), and a steplike cutout ( FIG. 6D ).
- turns of the fin 22 may be in any pattern as long as the embodiment achieves the objects of the present invention.
- FIGS. 7A to 7D and 8B show some patterns adoptable in the present invention, and the present invention may adopt these patterns.
- FIG. 7A shows a pattern in which lower portions of each heat transfer wall 23 connected to the turn 24 are cut out.
- FIG. 7B shows a pattern in which upper portions of each heat transfer wall 23 connected to the turn 24 are cut out.
- the melt water flows downward taking the shortcut route to facilitate drainage of the melt water compared with a conventional corrugated fin in which heat transfer walls 23 are provided almost entirely along the space between the tubes 21, 21.
- the heat transfer walls 23 are formed along the horizontal direction in the pattern in FIG. 7A , they may be inclined upward toward the middle in the width direction of the fin 22 as shown in FIG. 7C . Similarly, the heat transfer walls 23 in the pattern in FIG. 7B may be inclined downward toward the middle in the width direction of the fin 22 as shown in FIG. 7D . The drainage of the melt water can be further facilitated by thus inclining the heat transfer walls 23.
- the heat transfer pieces 23L on one side in the width direction X and the heat transfer pieces 23R on the other side are provided not to overlap with each other as seen in a vertical direction (as seen in a plan view), although the present invention is not limited to this.
- the heat transfer pieces 23L on the one side and the heat transfer pieces 23R on the other side may form overlaps K at the middle portion in the width direction X of the fin 22.
- This configuration also receives the above beneficial effect obtained by widening the fin pitch P1 of the above described area U because the fin pitch P1 of the heat transfer pieces 23L, 23L ... and the fin pitch P1 of the heat transfer pieces 23R, 23R ... within the area U close to the tubes 21 are twice as wide as the fin pitch P2 of the area D.
- the fin pitch P1 of the area U is widened by partially cutting out the fin workpiece 25, the present invention is not limited to this.
- the heat transfer pieces 23L, R may be folded downward to form regions corresponding to the cutouts. Then, the fin pitch P1 of the area U can be made wide compared with the fin pitch P2 of the area D similarly to the fin 22 of the first embodiment.
- Hanging pieces 23e formed by folding the heat transfer pieces each may be in contact with a surface of the heat transfer wall 23 on the lower layer at its tip as shown in FIG. 8C , or the tip may be away from the surface of the heat transfer wall 23 on the lower layer as shown in FIG. 8D which is not part of the presently claimed invention. In any case, the hanging pieces 23e contribute to facilitate drainage by forming paths for guiding the melt water downward.
- the heat transfer pieces may be folded at any angle.
- a louver 28 may be formed on the downwind side of the fin 22 (heat transfer wall 23) as shown in FIG. 9A (mode 2-1).
- the dehumidification can be performed also on the downwind side as a result of suppressing the dehumidification on the upwind side.
- a high heat transfer performance on the downwind side as in the mode 2-1 suppresses local frosting on the upwind side, thereby easily securing the ventilation paths 27.
- a duration of the heating operation can be extended because the heat exchanger 10 can exchange heat continuously on the downwind side.
- the upwind side of the fin 22 is not required to be processed, thereby suppressing increase in the processing cost.
- the louver 28 is formed by cutting and raising the heat transfer wall 23 and disturbing the flow of air passing over the louver 28 facilitates heat transfer between the air and the heat transfer wall 23. It is to be noted that the louver 28 facilitates heat transfer more effectively than undulations 29 that will be described later.
- the louver 28 may be provided at any region.
- the region is not limited to the downwind side but the louver 28 may be provided on the upwind side.
- the present invention can also improve heat transfer performance on the upwind side.
- the undulations 29 may be formed on the upwind side of the fin 22 (heat transfer wall 23) as shown in FIG. 9B (mode 2-2).
- the undulations 29 is wavy in a vertical cross section of the heat transfer wall 23 and has a shape of repeated mountain, valley, mountain ... from the upwind side to the downwind side.
- the louver 28 may be provided instead of the undulations 29 as shown in FIG. 9C for improving the heat transfer performance on the upwind side.
- an end of the fin 22 on the downwind side may be configured similarly to the end of the fin 22 on the upwind side according to the first embodiment. That is, as shown in FIGS. 10A to 10C , either of the opposite sides of the heat transfer wall 23 divided by the midpoint M in the width direction X is cut out. Because of the cutout, a leading edge portion 23d with the cutout is indented toward the upwind side relative to a leading edge portion 23c without the cutout. The leading edge portion 23c without the cutout is provided with heat transfer pieces 23L and 23R protruding toward the downwind side beyond the leading edge portion 23d. In addition, the heat transfer pieces 23L and 23R are each disposed on every other layer of the heat transfer wall 23, such that the heat transfer pieces 23L and 23R appear alternately on the opposite sides of the midpoint M in the width direction X.
- the third embodiment adopts a configuration of the widened fin pitch also on the downwind side to thereby reduce the amount of the melt water to accumulate on the downwind side. In this way, even if the remaining melt water solidifies after resumption of the heating operation, a heat transfer area of the fin 22 available for exchanging heat can be secured appropriately, and in addition, the ventilation path can be prevented from becoming easily clogged.
- the configuration of the widened fin pitch may adopt various forms as described in the first embodiment.
Description
- The present invention relates to a heat exchanger used for an air A heat exchanger according to the preamble of
claim 1 is known fromJPS 53 26694 - In an air conditioner that provides both cooling and heating by a common refrigeration cycle, one heat exchanger functions as a condenser during a cooling operation and as an evaporator during a heating operation.
- A heat exchanger in an outdoor unit functions as an evaporator during the heating operation. When the evaporator performs the heating operation during cold weather, for example, when the outside air temperature is as low as about -5°C, a frosting phenomenon occurs in the evaporator in which moisture in the air attaches to the evaporator as frost. Usually, frosting occurs from the upwind side of the heat exchanger, and the frost gradually grows toward the downwind side. If frosting occurs on the heat exchanger, a fin heat transfer area for directly exchanging heat with the air is reduced, thereby reducing a heating capability. In addition, the frosting narrows a ventilation path between fins to reduce the volume of air, which also reduces the heating capability. Accordingly, a defrosting operation is performed, for example, regularly, for removing the attached frost during the heating operation in a low outside air temperature. The heating operation is stopped during the defrosting operation, which might decrease the comfort of a user of the air conditioner. Hence, various techniques have been proposed for reducing likelihood of frosting on the upwind side of a heat exchanger (evaporator). Here, representative examples of the defrosting operation include melting the frost by switching the refrigeration cycle into the one in the cooling operation and working the outdoor heat exchanger as a condenser, and then flowing a high temperature refrigerant.
- In addition to the problem of frosting on the upwind side of the heat exchanger, water generated when frost is melted by the defrosting operation (melt water, hereinafter) is not drained entirely during the defrosting operation, and sometimes remains on the fins. If the heating operation is resumed after the defrosting operation with the melt water accumulating on the fins, the melt water freezes to cause frosting again, thereby easily clogging the ventilation path.
- The present inventors have disclosed in Patent Literature 1 a heat exchanger that inhibits frosting during the heating operation while facilitating drainage of melt water generated by the defrosting operation. In the proposal, the fin has thermal conduction control portions extending along a direction of an outside air flow. According to the heat exchanger of
Patent Literature 1, heat conduction from tubes to the fin is controlled on the upwind side in the direction of the outside air flow relative to the downwind side. The proposal ofPatent Literature 1, therefore, suppresses temperature drop of the fin at portions on the upwind side in the outside air flow direction when the heat exchanger in an outdoor unit functions as an evaporator, thereby controlling frosting. Also, the heat exchanger inPatent Literature 1 drains melt water downward through slits formed as thermal conduction control portions during the defrosting operation, and thus has excellent drainage.
Patent Literature 2, 3 and 4 each disclose other examples of heat exchangers. -
- Patent Literature 1: Japanese Patent Laid-Open No.
2012-72955 - Patent Literature 2:
JP 2002 130973 - Patent Literature 3:
JP S59 18179 - Patent Literature 4:
JP H06 347185 - The present invention aims to provide a heat exchanger that can, even when frosting occurs on the upwind side of the heat exchanger, exchange heat continuously on the downwind side of a fin by securing a ventilation path, and in addition, further improve drainage of melt water, from a different viewpoint than that in
Patent Literature 1. - To achieve the above object, a heat exchanger of the present invention is defined in
claim 1, and includes a plurality of tubes each having a flowpath through which a refrigerant flows, and a corrugated fin including a plurality of heat transfer walls that are arranged in a running direction of the tubes and span from one to the other of adjacent tubes among the plurality of tubes, the fin being capable of exchanging heat with the tubes. The heat transfer walls in the present invention include a first heat transfer piece leading to a first edge portion positioned on an upwind side of a passing airflow, and a second edge portion indented relative to the first edge portion toward a downwind side in a direction of the airflow, and the first heat transfer piece is disposed at least on every other layer of the arrangement of the heat transfer walls. - The heat exchanger of the present invention includes the heat transfer walls including a first edge portion and a second edge portion indented toward the downwind side relative to the first edge portion, and the first edge portion and the second edge portion are each disposed at least on every other layer in the direction of the arrangement. Accordingly, a fin pitch between the first edge portions adjacent to each other in the arrangement direction can be widened. As a result, even if frosting occurs locally on the first edge portions positioned on an upwind side end of the fin, the heat exchanger can exchange heat continuously on the downwind side because the ventilation path is secured.
- Because, in the heat exchanger of the present invention, the second edge portions are present that are indented toward the downwind side, the heat transfer walls are discontinuous on the upwind side relative to the second edge portion. This shortens the distance for the melt water generated during the defrosting operation to flow down the fin. Accordingly, the heat exchanger of the present invention drains the melt water to the outside of the heat exchanger in a short time compared with a heat exchanger in which the melt water flows down the fin while meandering. Additionally, in the heat exchanger of the present invention, the discontinuation of the heat transfer walls reduces boundary portions with the tubes where the melt water is particularly likely to accumulate, thereby reducing the accumulation amount of the melt water. Therefore, a heat transfer area of the fin can be secured appropriately even if the melt water solidifies after resumption of the heating operation.
- Each heat transfer wall in the present invention includes the first heat transfer piece leading to the first edge portion positioned on the upwind side of the passing airflow, and the second edge portion indented relative to the first edge portion toward the downwind side in the direction of the airflow, and the first heat transfer piece may be disposed alternately on the side closer to one tube and on the side closer to the other tube of adjacent tubes.
- In the heat exchanger of the present invention, the heat transfer walls include the first edge portion and the second edge portion indented toward the downwind side relative to the first edge portion, and the first edge portion and the second edge portion are disposed alternately in the arrangement direction of the heat transfer walls. Accordingly, there is a portion without a heat transfer wall between the first edge portions adjacent in the arrangement direction for the second edge portions are indented toward the downwind side, thereby widening the fin pitch. As a result, even if frosting occurs locally on the first edge portions positioned on an upwind side end of the fin, the heat exchanger can exchange heat continuously on the downwind side because the ventilation path is secured.
- In the present invention, the heat transfer walls are each preferably equipped with heat transfer facilitating means on the upwind side.
- Provision of the heat transfer facilitating means on the upwind side improves the heat transfer performance of the heat transfer walls on the upwind side.
- Further, in the present invention, the heat transfer walls are each preferably equipped with heat transfer facilitating means on the downwind side.
- Provision of the heat transfer facilitating means on the downwind side improves the heat transfer performance of the heat transfer walls on the downwind side.
- In the present invention, each of the heat transfer walls preferably includes a second heat transfer piece leading to a third edge portion positioned on the downwind side of the airflow, and a fourth edge portion indented toward the upwind side relative to the third edge portion, and the second heat transfer piece is preferably disposed on every other layer of the arrangement on both of a side closer to one tube and a side closer to the other tube of adjacent tubes such that the second heat transfer piece appears alternately on both sides.
- Because there is a region without a heat transfer wall also on the downwind side, the drainage of the melt water can be improved also on the downwind side. Further, even if the remaining melt water solidifies, a heat transfer area of the fin available for exchanging heat directly with the air can be secured appropriately, and in addition, the ventilation path can be prevented from becoming easily clogged.
- A heat exchanger structure of the present invention is a collection of a plurality of heat exchangers arranged in the direction of the passing airflow, the heat exchangers including a plurality of tubes arranged in a predetermined direction, the tubes each including a flowpath through which a refrigerant flows, and a corrugated fin provided between adjacent tubes among the plurality of tubes, the fin being capable of exchanging heat with the tubes. Among the heat exchangers, one disposed on the most upwind side in the direction of the airflow is the heat exchanger according to the present invention.
- By providing the heat exchanger according to the present invention on the most upwind side in the direction of the airflow, the airflow is dehumidified while it passes through the heat exchanger on the upwind side, which reduces the frosting to the following heat exchangers.
- A fin for heat exchanger used in the heat exchanger of the present invention is a corrugated fin that is provided between adjacent tubes and is capable of exchanging heat with the tubes.
- According to the present invention, by widening the fin pitch of the corrugated fin in the area close to the end positioned on the upwind side, the portion with the wide fin pitch is secured as the ventilation path even if frosting occurs locally on the first edge portion, which is an end of the fin, and thus the heat exchanger can exchange heat continuously on the downwind side of the fin. In an air conditioner using the heat exchanger of the present invention, therefore, the time between defrosting operations is increased, thereby decreasing the frequency of the defrosting operation.
- According to the present invention, the first edge portion and the second edge portion are disposed alternately in the direction of the heat transfer wall arrangement, allowing the melt water to be drained to the outside of the heat exchanger in a short time. Thus, the drainage of the melt water can be improved. Further, according to the present invention, because the amount of the melt water to accumulate is reduced, a heat transfer area of the fin can be secured appropriately even if the melt water solidifies after resumption of the heating operation.
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- [
FIG. 1] FIG. 1 is a perspective view showing a heat exchanger according to an embodiment of the present invention. - [
FIG. 2] FIG. 2 is a partially exploded perspective view showing a heat exchanger according to a first embodiment of the present invention. - [
FIGS. 3A to 3C] FIGS. 3A to 3C show the heat exchanger of the first embodiment in whichFIG. 3A is a plan view showing an area between adjacent tubes,FIG. 3B is a view schematically showing a side cross section of a fin, andFIG. 3C is a developed view of the fin. - [
FIG. 4] FIG. 4 is a schematic view explaining the effects of the first embodiment. - [
FIGS. 5A to 5D] FIGS. 5A to 5D are schematic views explaining the effects of the first embodiment in whichFIG. 5A shows a side cross section of the fin of the embodiment,FIG. 5B shows a side cross section of a conventional fin,FIG. 5C shows a side cross section of the heat exchanger of the embodiment, andFIG. 5D shows a side cross section of a conventional heat exchanger. - [
FIGS. 6A to 6D] FIGS. 6A to 6D are perspective views showing a modification of the fin in the first embodiment. - [
FIGS. 7A to 7D] FIGS. 7A to 7D is a side cross-sectional view showing another modification of the fin in the first embodiment. - [
FIG. 8B] FIG. 8B is a side cross-sectional view showing still another modification of the fin in the first embodiment. - [
FIGS. 8A, 8C and 8D] FIGS. 8A, 8C and 8D are side cross-sectional views showing still another modification of the fin in the first embodiment that are not part of the presently claimed invention. - [
FIGS. 9A to 9C] FIGS. 9A to 9C are partially exploded perspective views showing a heat exchanger according to a second embodiment of the present invention in whichFIG. 9A shows an example of providing a louver on the downwind side;FIG. 9B shows an example of providing undulations on the upwind side and a louver on the downwind side, andFIG. 9C shows an example of providing louvers on both the upwind side and the downwind side. - [
FIGS. 10A to 10C] FIGS. 10A to 10C show a heat exchanger according to a third embodiment of the present invention in whichFIG. 10A is a partially exploded perspective view,FIG. 10B is a plan view showing an area between adjacent tubes, andFIG. 10C is a developed view of a fin. - [
FIG. 11] FIG. 11 is a perspective view showing a heat exchanger structure according to a fourth embodiment of the present invention. - [
FIGS. 12A and 12B] FIGS. 12A and 12B are views showing a modification of the present invention. - Hereinafter, embodiments of the heat exchanger of the present invention will be described with reference to the drawings.
- As shown in
FIGS. 1 to 3C , aheat exchanger 10 in the embodiment includes a core 20 formed by alternately stacking a plurality oftubes 21 though which a refrigerant flows and a plurality offins 22, and a pair ofheader tubes 30 to which ends of thetubes 21 are connected, and exchanges heat between an outside air and the refrigerant. - The
heat exchanger 10 is applied to an outdoor heat exchanger of a heat pump air conditioner. In that case, theheat exchanger 10 is assembled to an outdoor unit of the air conditioner with thetubes 21 standing along a vertical direction Y. Theheat exchanger 10 receives an airflow A generated by a fan that is omitted in the drawings, and exchanges heat between the refrigerant and the outside air while the airflow passes throughventilation paths 27, openings formed between thetubes 21 and thefins 22 of thecore 20. - The
tubes 21 each have a flat cross section and include a flowpath for a refrigerant penetrating therethrough in the axial direction. Thetubes 21 are manufactured by extruding copper or a copper alloy, or aluminum or an aluminum alloy that have excellent thermal conductivity, or by roll forming a plate-like material. - The
tubes 21 have their both axial ends joined to eachheader tube 30 by soldering, for example, and therefrigerant flowpaths 21a formed inside thetubes 21 along the axial direction are in communication with a refrigerant flowpath of eachheader tube 30 that will be described later. This ensures a flow of the refrigerant between thetubes 21 and theheader tubes 30. - In the embodiment, the
fins 22 use corrugated fins each formed by repeated alternate mountain folds and valley folds. Eachfin 22 includes aheat transfer wall 23 and aturn 24 connectingheat transfer walls heat transfer walls heat transfer wall 23 is treated as one layer. - The
turn 24 has a rectangular shape in the example, although theturn 24 may be in other configurations, such as a V shape. Thefin 22 is integrally formed by a fold forming a plate-shaped workpiece made from a material similar to that of thetubes 21. Thefin 22 is characterized in the configuration on its upwind side, which will be described later. - The
core 20 is constituted by the above describedtubes 21 and thefin 22, which are stacked alternately in the width direction X of theheat exchanger 10. Thefin 22 arranged betweentubes tubes turns 24 by, for example, soldering, allowing thefin 22 and thetubes 21 to exchange heat with each other. Thecore 20 is provided withside plates 26 on both ends in the width direction X. Theside plates 26 each function as a reinforcing member of the core 20, and are supported by theheader tubes 30 at both end portions in the up-down direction. - The
header tubes 30 each have a refrigerant flowpath (not shown) inside. - For example, the
header tube 30 placed on the lower side in the figure (a lower header tube 32) is provided with an inlet of the refrigerant at one end side in the width direction X. The refrigerant supplied through refrigerant tubing forming the refrigeration cycle to the inlet passes through the flowpath in thelower header tube 32 and flows into the plurality oftubes 21. Theheader tube 30 placed on the upper side in the figure (an upper header tube 31) is provided with an outlet of the refrigerant at one end side in the width direction X. The refrigerant having flown through thetubes 21 flows into theupper header tube 31 and flows through the outlet toward the refrigerant tubing forming the refrigeration cycle. - The
header tubes 30 may be manufactured from a material similar to that of thetubes 21. Thetubes 21 may be manufactured integrally or may be manufactured by combining several members. - If an air conditioner including the
heat exchanger 10 as an outdoor heat exchanger is performing the heating operation in a low outside air temperature, frosting occurs on thefin 22 on the upwind side of the airflow A. It is to be noted that, hereinafter, the upwind side of the airflow A may simply be referred to as the upwind side for short. The same applies to the downwind side. The air conditioner performs a defrosting operation, for example, regularly for removing the attached frost. If the melt water remains not being fully drained from theheat exchanger 10 after the defrosting operation, it might freeze after resumption of the heating operation, possibly causing frosting again. - In the
heat exchanger 10, a fin pitch at the upwind side of thefins 22 is made wider than that at the downwind side. This allows theheat exchanger 10 to exchange heat continuously on the downwind side even when the frosting occurs, increasing an interval between the defrosting operations. Also, theheat exchanger 10 provides improved drainage of the melt water. Hereinafter, the characteristics of thefin 22 will be described with reference toFIGS. 2 to 4 . InFIG. 3B , a side cross section of thefin 22 at an area U on the upwind side is shown by solid lines and a side cross section of thefin 22 at an area D on the downwind side is shown by dashed lines. The same applies toFIGS. 5A to 5D , and7A to 9C . - In the
fin 22, a fin pitch P1 at a predetermined area U (FIG. 3A ) on the upwind side is set wider than a fin pitch P2 at an area D on the downwind side relative to the area U, as shown inFIGS. 2 to 3C . - Each
heat transfer wall 23 of thefin 22 satisfies the following two conditions for widening the fin pitch P1 compared with the fin pitch P2. - A first condition is that either of the opposite sides of the
heat transfer wall 23 divided by the midpoint M in the width direction X is cut out. Because of the cutout, aleading edge portion 23b with the cutout is indented toward the downwind side relative to aleading edge portion 23a without the cutout. Theleading edge portion 23a without the cutout is provided with aheat transfer piece leading edge portion 23b. - A second condition is that the
heat transfer pieces heat transfer wall 23, such that theheat transfer pieces heat transfer wall 23, alternately on the opposite sides of the midpoint M in the width direction X. - By satisfying the above two conditions, in the area U of the
fin 22, theheat transfer piece 23L is provided on every other layer on one side (left side ofFIG. 3B ) L of the midpoint M. Similarly, also on the other side (right side ofFIG. 3B ) R, theheat transfer piece 23R is provided on every other layer. In addition, the phase of the fin pitch P1 is shifted by 1/2 cycle (half cycle) between the one side L and the other side R. - It is to be noted that although portions of the
heat transfer pieces tubes 21 are cut out, and thus thefin 22 has noturns 24 in the area U, the portions however may not be cut out to leave the turns. Theheat transfer pieces tubes 21 at their edges facing thetubes 21 by soldering such that theheat transfer pieces tubes 21, or may be separated from thetubes 21. - A
fin workpiece 25 used for forming thefin 22 is formed from a plate of the above described metal material in the shape of a rectangular in a plan view, as shown inFIG. 3C . Thefin workpiece 25 has a plurality of evenly spacedrectangular cutouts 25a at an edge corresponding to the upwind side when assembled as thefin 22 to theheat exchanger 10. Eachworkpiece portion 25b remaining betweenadjacent cutouts heat transfer piece fin workpiece 25 has on the edge thecutouts 25a and theworkpiece portions 25b that are repeatedly formed in an alternate manner. - Next, the operation and effects of the
heat exchanger 10 including the forgoingfin 22 will be described. - First, a description will be given on how the
heat exchanger 10 exchanges heat continuously on the downwind side with reference toFIG. 4 . - In the
fin 22, the fin pitch P1 at the area U positioned on the upwind side is made wider than the fin pitch P2 at the area D positioned on the downwind side. As shown inFIG. 4 , frosts Fa formed locally on theleading edge portions 23a of theheat transfer walls 23 positioned on the upwind side narrows theventilation paths 27, but the wide fin pitch P1 can extend the time to clogging on the upwind side by the frosts Fa. - Also, even if frosts Fb attach to the
leading edge portions 23b, openings that function as theventilation paths 27 are secured between the frosts Fa and the frosts Fb for a long time because theleading edge portions 23b are indented toward the downwind side. In particular, the airflow A having reached theleading edge portions 23b contains a reduced amount of moisture as it is dehumidified by the leadingedge portions 23a, and therefore, an amount of the frosts Fb on theleading edge portions 23b is less than that on theleading edge portions 23a. This is advantageous in securing openings functioning as theventilation paths 27. - As described above, the
heat exchanger 10 can exchange heat continuously within the area D on the downwind side of thefin 22 for a long time. As a result, an air conditioner using theheat exchanger 10 can decrease the frequency of the defrosting operation. - On the other hand, because the area D has a higher density of the
heat transfer wall 23 than that in the area U, thefin 22 can minimize a reduction in heat exchange efficiency. - Next, the improvement in the drainage of melt water will be described with reference to
FIGS. 5A to 5D . The improvement of the drainage in the present invention includes reducing the amount of melt water to accumulate in addition to facilitating the drainage itself. - First, the facilitation of the drainage will be described.
- Because the
heat exchanger 10 is provided with theleading edge portions 23b that are indented toward the downwind side, theheat transfer walls 23 are discontinuous on the upwind side (area U) of thefin 22. As a result, melt waters W generated as frosts F melt during the defrosting operation flow off both sides of theheat transfer pieces FIG. 5A . The melt waters W flow down the tubes 21 (not shown inFIG. 5A ) on the sides opposed to thetubes 21, and drop directly downward on the sides facing the cutout to be discharged to the outside of theheat exchanger 10. In contrast, if there is noleading edge portion 23b indented toward the downwind side, as shown inFIG. 5B , the melt water W would flow down thefin 22 while meandering, as shown by an arrow Wf. In this way, theheat exchanger 10 can remove the melt water W to the outside of theheat exchanger 10 in a short time compared with draining while meandering, because theheat exchanger 10 can drain the melt water W taking a shortcut route. - Next, the reduction of the accumulation will be described.
- The melt water W that has not been drained is likely to accumulate at the inside IN of the
turns 24 as shown inFIG. 5D . In theheat exchanger 10, however, the leadingedge portions 23b are indented toward the downwind side and there are no insides IN of theturns 24 within the area U on the upwind side, where frosting easily occurs, and thus, if the melt water W accumulates, it only accumulates above the boundaries between theheat transfer pieces tubes 21 as shown inFIG. 5C . According to theheat exchanger 10, therefore, because the amount of the melt water W to accumulate on thefin 22 can be reduced, even if the melt water W solidifies after resumption of the heating operation, a wider heat transfer area of thefin 22 can be secured and also the ventilation path can be prevented from becoming easily clogged. - Also, the
heat exchanger 10 can ensure a desired heat transfer performance within the area U if theheat transfer pieces tubes 21 such that theheat transfer pieces tubes 21. - Some modifications of the embodiment will be described.
- Although the cutouts of the
fin 22 of the embodiment each have a rectangular shape as seen in a plan view, the cutouts may have any shape as long as the embodiment achieves the objects of the present invention. For example, as shown inFIGS. 6A to 6D , the cutouts may adopt several shapes including a circular cutout (FIG. 6A ), a triangular cutout (FIG. 6B ), a polygonal cutout (FIG. 6C ), and a steplike cutout (FIG. 6D ). - Also, the turns of the
fin 22 may be in any pattern as long as the embodiment achieves the objects of the present invention.FIGS. 7A to 7D and8B show some patterns adoptable in the present invention, and the present invention may adopt these patterns. -
FIG. 7A shows a pattern in which lower portions of eachheat transfer wall 23 connected to theturn 24 are cut out. In contrast,FIG. 7B shows a pattern in which upper portions of eachheat transfer wall 23 connected to theturn 24 are cut out. In any one of the patterns inFIG. 7A and 7B , the melt water flows downward taking the shortcut route to facilitate drainage of the melt water compared with a conventional corrugated fin in which heattransfer walls 23 are provided almost entirely along the space between thetubes - Although the
heat transfer walls 23 are formed along the horizontal direction in the pattern inFIG. 7A , they may be inclined upward toward the middle in the width direction of thefin 22 as shown inFIG. 7C . Similarly, theheat transfer walls 23 in the pattern inFIG. 7B may be inclined downward toward the middle in the width direction of thefin 22 as shown inFIG. 7D . The drainage of the melt water can be further facilitated by thus inclining theheat transfer walls 23. - Next, in the
fin 22 of the first embodiment, theheat transfer pieces 23L on one side in the width direction X and theheat transfer pieces 23R on the other side are provided not to overlap with each other as seen in a vertical direction (as seen in a plan view), although the present invention is not limited to this. - As shown in
FIG. 8A which is not part of the presently claimed invention, theheat transfer pieces 23L on the one side and theheat transfer pieces 23R on the other side may form overlaps K at the middle portion in the width direction X of thefin 22. This configuration also receives the above beneficial effect obtained by widening the fin pitch P1 of the above described area U because the fin pitch P1 of theheat transfer pieces heat transfer pieces tubes 21 are twice as wide as the fin pitch P2 of the area D. - Alternatively, in the present invention, gaps G may be provided at the middle portion in the width direction X of the
fin 22 between theheat transfer pieces 23L on the one side and theheat transfer pieces 23R on the other side as shown inFIG. 8B which is part of the presently claimed invention. Similarly toFIG. 8A , this configuration also receives the beneficial effect obtained by widening the fin pitch P1 of the area U. - Next, although in the
fin 22 of the first embodiment, the fin pitch P1 of the area U is widened by partially cutting out thefin workpiece 25, the present invention is not limited to this. - As shown in
FIG. 8C which is not part of the presently claimed invention, theheat transfer pieces 23L, R may be folded downward to form regions corresponding to the cutouts. Then, the fin pitch P1 of the area U can be made wide compared with the fin pitch P2 of the area D similarly to thefin 22 of the first embodiment. Hangingpieces 23e formed by folding the heat transfer pieces each may be in contact with a surface of theheat transfer wall 23 on the lower layer at its tip as shown inFIG. 8C , or the tip may be away from the surface of theheat transfer wall 23 on the lower layer as shown inFIG. 8D which is not part of the presently claimed invention. In any case, the hangingpieces 23e contribute to facilitate drainage by forming paths for guiding the melt water downward. Here, the heat transfer pieces may be folded at any angle. - Next, the
fin 22 may be provided with means for improving the heat transfer performance of one or both of the upwind side and the downwind side, as will be described below. - As an example, a
louver 28 may be formed on the downwind side of the fin 22 (heat transfer wall 23) as shown inFIG. 9A (mode 2-1). - If the
fin 22 has a higher heat transfer performance on the downwind side than on the upwind side, the dehumidification can be performed also on the downwind side as a result of suppressing the dehumidification on the upwind side. Here, because frosting is partly caused by the dehumidification by thefin 22, a high heat transfer performance on the downwind side as in the mode 2-1 suppresses local frosting on the upwind side, thereby easily securing theventilation paths 27. Thus, according to the mode 2-1, in addition to alleviating the decrease in the heating capability due to reduction in the volume of air, a duration of the heating operation can be extended because theheat exchanger 10 can exchange heat continuously on the downwind side. At the same time, the upwind side of thefin 22 is not required to be processed, thereby suppressing increase in the processing cost. - The
louver 28 is formed by cutting and raising theheat transfer wall 23 and disturbing the flow of air passing over thelouver 28 facilitates heat transfer between the air and theheat transfer wall 23. It is to be noted that thelouver 28 facilitates heat transfer more effectively than undulations 29 that will be described later. - The
louver 28 may be provided at any region. The region is not limited to the downwind side but thelouver 28 may be provided on the upwind side. - The present invention can also improve heat transfer performance on the upwind side.
- As an example, the
undulations 29 may be formed on the upwind side of the fin 22 (heat transfer wall 23) as shown inFIG. 9B (mode 2-2). Theundulations 29 is wavy in a vertical cross section of theheat transfer wall 23 and has a shape of repeated mountain, valley, mountain ... from the upwind side to the downwind side. - Because a heat transfer area is increased on the upwind side by forming the
undulations 29 on the upwind side, the heat transfer performance is increased compared with a fin formed by a flat plate. In addition, vortexes are generated when the airflow passes through theundulations 29, which also improves the heat transfer performance. - The
louver 28 may be provided instead of theundulations 29 as shown inFIG. 9C for improving the heat transfer performance on the upwind side. - In the present invention, an end of the
fin 22 on the downwind side may be configured similarly to the end of thefin 22 on the upwind side according to the first embodiment. That is, as shown inFIGS. 10A to 10C , either of the opposite sides of theheat transfer wall 23 divided by the midpoint M in the width direction X is cut out. Because of the cutout, aleading edge portion 23d with the cutout is indented toward the upwind side relative to aleading edge portion 23c without the cutout. Theleading edge portion 23c without the cutout is provided withheat transfer pieces leading edge portion 23d. In addition, theheat transfer pieces heat transfer wall 23, such that theheat transfer pieces - Because the frosting also occurs on the downwind side of the
fin 22 although in a smaller amount than on the upwind side, the defrosting operation can lead to the accumulation of the melt water also on the downwind side of thefin 22. Then, the third embodiment adopts a configuration of the widened fin pitch also on the downwind side to thereby reduce the amount of the melt water to accumulate on the downwind side. In this way, even if the remaining melt water solidifies after resumption of the heating operation, a heat transfer area of thefin 22 available for exchanging heat can be secured appropriately, and in addition, the ventilation path can be prevented from becoming easily clogged. - The configuration of the widened fin pitch may adopt various forms as described in the first embodiment.
- As shown in
FIG. 11 , the air conditioner may have a plurality of air conditioners 10 (10a and 10b) that are arranged (two air conditioners in the figure) in the direction of the wind flow for achieving a high heat transfer performance. The present invention can be applied to an air conditioner having a plurality ofheat exchangers 10. - It is to be noted that the
heat exchanger 10a disposed on the upwind side should adopt the present invention, while there is less need to apply the present invention to theheat exchanger 10b disposed on the downwind side. This is because the airflow having passed through theheat exchanger 10a on the upwind side flows into theheat exchanger 10b on the downwind side during the defrosting operation, and the airflow causes little or almost no frosting for the airflow has been dehumidified as it passed through theheat exchanger 10a on the upwind side. Of course, it does not intend to eliminate application of the present invention to theheat exchanger 10b on the downwind side. However, it agrees with the aim of providing the plurality of heat exchangers that theheat exchanger 10b on the downwind side appropriately secures a heat transfer area and minimizes a loss of the heat transfer performance. - Not only in the case of an air conditioner having two heat exchangers, but also in a case of an air conditioner having three or more heat exchangers, it is enough to apply the present invention to the heat exchanger disposed on the most upwind side. The term "application of the present invention", as used herein, includes all individual elements disclosed in the foregoing first to third embodiments.
- The embodiments of the present invention have been described hereinbefore. However, some configurations may be selected from those cited in the above embodiments or may be appropriately changed to other configurations, without departing from the scope of the appended claims.
- For example, the effects of the widened fin pitch and improved melt water drainage can be achieved even when both widthwise sides of the
heat transfer walls 23 are cut out as shown inFIG. 12A . Alternatively, theheat transfer pieces 23L and theheat transfer pieces 23R each can be disposed on every three layers, for example, as shown inFIG. 12B . -
- 10, 10a, 10b Heat exchanger
- 20 Core
- 21 Tube
- 21a Refrigerant flowpath
- 22 Fin
- 23 Heat transfer wall
- 23L, 23R Heat transfer piece
- 23a to 23d Leading edge portion
- 23e Hanging piece
- 25 Fin workpiece
- 25b Workpiece portion
- 26 Side plate
- 27 Ventilation path
- 28 Louver
- 29 Undulations
- 30 Header tube
- 31 Upper header tube
- 32 Lower header tube
- A Airflow
- F, Fa, Fb Frost
- G Gap
- IN Inside
- M Midpoint
- P1 Fin pitch
- P2 Fin pitch
- D, U Area
- W Melt water
- X Width direction
- Y Vertical direction
Claims (5)
- A heat exchanger (10; 10a, 10b) comprising:a plurality of tubes (21) each having a flowpath (21a) through which a refrigerant flows; anda corrugated fin (22) including a plurality of heat transfer walls (23) that are arranged in a running direction of the tubes (21) and span from one to the other of adjacent tubes (21) among the plurality of tubes (21), the fin (22) being capable of exchanging heat with the tubes (21), the heat transfer walls (23) that are arranged in a running direction of the tubes (21) and span from one to the other of adjacent tubes (21) among the plurality of tubes (21) defining an arrangement of heat transfer walls (23), whereinthe heat transfer walls (23) each include:a first heat transfer piece (23L) leading to a first edge portion (23a) positioned on an upwind side of a passing airflow (A); anda second heat transfer piece (23R) leading to a second edge portion (23b) indented relative to the first edge portion (23a) toward a downwind side in a direction of the airflow (A),wherein the first edge portion (23a) and the second edge portion (23b) are both arranged on the upwind side of the airflow (A), andwherein the first heat transfer piece (23L) is disposed at least on every other layer of the arrangement of heat transfer walls (23) on both of a side closer to one tube (21) and the second heat transfer piece (23R) is disposed at least on every other layer of the arrangement of heat transfer walls (23) on both of a side closer to the other tube (21) of adjacent tubes (21) among the plurality of tubes (21) such that first heat transfer piece (23L) and the second heat transfer piece (23R) appears alternately on both sides, andwherein a first fin pitch (P1) at a predetermined area (U) on the upwind wide is set wider than a second fin pitch (P2) at an area (D) on the downwind side relative to the predetermined area (U), andcharacterized in that the first heat transfer piece (23L) and the second heat transfer piece (23R) are provided not to overlap with each other as seen in a vertical direction.
- The heat exchanger (10; 10a, 10b) according to claim 1, wherein
the heat transfer walls (23) include
heat transfer facilitating means (28; 29) on the upwind side. - The heat exchanger (10; 10a, 10b) according to any one of claims 1 or 2, wherein
the heat transfer walls (23) include
heat transfer facilitating means (28) on the downwind side. - The heat exchanger (10; 10a, 10b) according to any one of claims 1 to 3, wherein
the first heat transfer piece (23L) of each of the heat transfer walls (23) leads to a third edge portion (23c) positioned on the downwind side of the airflow (A); and
each of the second heat transfer piece (23R) further leads to a fourth edge portion (23d) indented toward the upwind side relative to the third edge portion (23c). - A heat exchanger structure that is a collection of a plurality of heat exchangers (10; 10a, 10b) arranged in a direction of a passing airflow, the heat exchangers (10; 10a, 10b) including:a plurality of tubes (21) arranged in a predetermined direction, the tubes (21) each including a flowpath (21a) through which a refrigerant flows; anda corrugated fin (22) provided between adjacent tubes (21) among the plurality of tubes (21), the fin (22) being capable of exchanging heat with the tubes (21), whereinamong the heat exchangers (10; 10a, 10b), one disposed on a most upwind side in the direction of the airflow (A) is the heat exchanger (10; 10a, 10b) according to any one of claims 1 to 4.
Applications Claiming Priority (1)
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PCT/JP2013/004041 WO2014207785A1 (en) | 2013-06-28 | 2013-06-28 | Heat exchanger, heat exchanger structure, and fin for heat exchanger |
Publications (3)
Publication Number | Publication Date |
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EP3015808A1 EP3015808A1 (en) | 2016-05-04 |
EP3015808A4 EP3015808A4 (en) | 2016-07-27 |
EP3015808B1 true EP3015808B1 (en) | 2018-08-29 |
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EP13888478.8A Active EP3015808B1 (en) | 2013-06-28 | 2013-06-28 | Heat exchanger, heat exchanger structure, and fin for heat exchanger |
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EP (1) | EP3015808B1 (en) |
JP (1) | JPWO2014207785A1 (en) |
WO (1) | WO2014207785A1 (en) |
Cited By (1)
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US11035623B2 (en) | 2018-03-02 | 2021-06-15 | Hitachi-Johnson Conrols Air Conditioning, Inc. | Heat exchanger, outdoor unit, refrigeration cycle device, and heat exchanger manufacturing method |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
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JP6771557B2 (en) * | 2016-07-07 | 2020-10-21 | 三菱電機株式会社 | Heat exchanger |
JP6758968B2 (en) * | 2016-07-14 | 2020-09-23 | 日立ジョンソンコントロールズ空調株式会社 | Heat exchanger |
CN110462309B (en) | 2017-03-27 | 2022-03-01 | 大金工业株式会社 | Heat exchanger and refrigerating apparatus |
JP6766722B2 (en) | 2017-03-27 | 2020-10-14 | ダイキン工業株式会社 | Heat exchanger or refrigeration equipment |
JP6766723B2 (en) | 2017-03-27 | 2020-10-14 | ダイキン工業株式会社 | Heat exchanger or refrigeration equipment |
JP6880901B2 (en) | 2017-03-27 | 2021-06-02 | ダイキン工業株式会社 | Heat exchanger unit |
US11415371B2 (en) | 2017-03-27 | 2022-08-16 | Daikin Industries, Ltd. | Heat exchanger and refrigeration apparatus |
JP6734002B1 (en) * | 2019-11-11 | 2020-08-05 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
WO2021095538A1 (en) * | 2019-11-11 | 2021-05-20 | 三菱電機株式会社 | Heat exchanger, refrigeration cycle device, and method for producing corrugated fin |
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JPS5916955U (en) * | 1982-07-23 | 1984-02-01 | カルソニックカンセイ株式会社 | Evaporator |
JPS5918179U (en) * | 1982-07-26 | 1984-02-03 | カルソニックカンセイ株式会社 | Evaporator |
JPS5994270U (en) * | 1982-12-16 | 1984-06-26 | 昭和アルミニウム株式会社 | Condensation water drainage device in evaporator |
JPH0396582U (en) * | 1989-12-27 | 1991-10-02 | ||
JPH06347185A (en) * | 1993-06-07 | 1994-12-20 | Matsushita Refrig Co Ltd | Heat exchanger |
JP2002130973A (en) * | 2000-10-25 | 2002-05-09 | Zexel Valeo Climate Control Corp | Heat exchanger |
JP2005106328A (en) * | 2003-09-29 | 2005-04-21 | Sanden Corp | Heat exchanging device |
DE102005044754A1 (en) * | 2005-09-20 | 2007-03-29 | Behr Gmbh & Co. Kg | Heat exchanger has two or more rows of flat pipes with pipes of one row off-set relative to pipes of adjoining row and welded to corrugated fins |
JP4674602B2 (en) * | 2007-11-22 | 2011-04-20 | 株式会社デンソー | Heat exchanger |
IN2012DN00867A (en) * | 2009-09-16 | 2015-07-10 | Carrier Corp | |
JP5936297B2 (en) | 2010-09-29 | 2016-06-22 | 三菱重工業株式会社 | Heat exchanger |
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2013
- 2013-06-28 EP EP13888478.8A patent/EP3015808B1/en active Active
- 2013-06-28 JP JP2015523665A patent/JPWO2014207785A1/en active Pending
- 2013-06-28 WO PCT/JP2013/004041 patent/WO2014207785A1/en active Application Filing
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JPS506455U (en) * | 1973-05-12 | 1975-01-23 | ||
JP2009270792A (en) * | 2008-05-09 | 2009-11-19 | Sharp Corp | Heat exchanger |
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US11035623B2 (en) | 2018-03-02 | 2021-06-15 | Hitachi-Johnson Conrols Air Conditioning, Inc. | Heat exchanger, outdoor unit, refrigeration cycle device, and heat exchanger manufacturing method |
Also Published As
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WO2014207785A1 (en) | 2014-12-31 |
EP3015808A1 (en) | 2016-05-04 |
EP3015808A4 (en) | 2016-07-27 |
JPWO2014207785A1 (en) | 2017-02-23 |
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