EP3051244A1 - Wärmetauscher und klimaanlage damit - Google Patents
Wärmetauscher und klimaanlage damit Download PDFInfo
- Publication number
- EP3051244A1 EP3051244A1 EP14847978.5A EP14847978A EP3051244A1 EP 3051244 A1 EP3051244 A1 EP 3051244A1 EP 14847978 A EP14847978 A EP 14847978A EP 3051244 A1 EP3051244 A1 EP 3051244A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- column
- heat exchanger
- heat
- refrigerant
- porous flat
- 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.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 112
- 238000005192 partition Methods 0.000 claims abstract description 35
- 238000004378 air conditioning Methods 0.000 claims description 6
- 239000007788 liquid Substances 0.000 description 35
- 239000012530 fluid Substances 0.000 description 16
- 239000007789 gas Substances 0.000 description 8
- 230000000694 effects Effects 0.000 description 4
- 239000012141 concentrate Substances 0.000 description 3
- 230000005484 gravity Effects 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- RTZKZFJDLAIYFH-UHFFFAOYSA-N Diethyl ether Chemical compound CCOCC RTZKZFJDLAIYFH-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 238000000638 solvent extraction Methods 0.000 description 2
- 150000004996 alkyl benzenes Chemical class 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 239000010696 ester oil Substances 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000010721 machine oil Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0015—Heat and mass exchangers, e.g. with permeable walls
Definitions
- the present invention relates to a heat exchanger having a plurality of columns of heat transfer tubes through which refrigerant flows in the flow direction of a heat-exchange fluid (such as air).
- a heat-exchange fluid such as air
- Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2003-287390 (see Fig. 4 and other related information)
- Fig. 8 shows an internal structure of a header 4 of a conventional heat exchanger as described above, and is a cross-sectional view of a column bridging portion 5 that allows the refrigerant to flow between the columns of heat transfer tubes.
- Fig. 8 (a) shows a liquid refrigerant flow 3 when the cross-sectional shape of the column bridging portion 5 is a rectangle
- Fig. 8 (b) shows the liquid refrigerant flow 3 when the cross-sectional shape of the column bridging portion 5 is a substantial parallelogram.
- two-phase gas-liquid refrigerant having a quality of approximately 0.5 flows out of a porous flat tube 2 on the windward side of air, which is a heat-exchange fluid, and flows into a porous flat tube 2 of the leeward column as indicated by the refrigerant flow 3.
- liquid refrigerant 6 in the two-phase gas-liquid refrigerant concentrates in a leeward side part in the vicinity of the porous flat tube 2 of the leeward column by inertia force from the outflow side-heat transfer tube.
- the present invention has been made to solve the above problem, and aims to provide a heat exchanger configured so that, when heat transfer tubes arranged in a column-wise direction are connected in a column bridging portion, which is a refrigerant flow path, the flow rate distribution of liquid refrigerant flowing into the heat transfer tube at and after the column bridging portion is even, or the flow rate distribution is appropriate to heat load, achieving excellent performance of the heat exchanger.
- a heat exchanger includes a heat transfer tube having an internal flow path through which a heat medium flows, the heat transfer tubes being arranged in a plurality of columns in a column-wise direction in which a heat-exchange medium passes through; a column bridging portion being a heat medium-flow path connecting a pair of the heat transfer tubes arranged adjacent to each other in the column-wise direction; a header to which the heat transfer tubes are connected, the column bridging portion being provided inside the header; and a refrigerant partition plate installed in the heat medium-flow path inside the column bridging portion.
- the refrigerant partition plate for guiding the flowing heat medium is provided inside the column bridging portion.
- the flow rate distribution of liquid refrigerant flowing into the heat transfer tube at and after the column bridging portion is made even, or the flow rate distribution becomes appropriate to heat load, achieving excellent performance of the heat exchanger.
- Fig. 1 is a partial front view of the heat exchanger according to Embodiment 1.
- Fig. 2 is a cross-sectional view of porous flat tubes of the heat exchanger according to Embodiment 1.
- the heat exchanger according to Embodiment 1 is a finned tube type heat exchanger.
- Heat transfer tubes of the heat exchanger are arranged in the horizontal direction, while fins 1 are arranged in the vertical direction.
- a header 4 is connected to one end side of the heat transfer tubes.
- the header 4 is arranged so that its axial direction is parallel to the gravity direction.
- the heat transfer tubes are a porous flat tubes 2 each having many refrigerant flow paths arranged in parallel, and are arranged in two columns in the flowing direction of air, which is a heat-exchange fluid.
- the porous flat tubes 2 in the two columns are arranged in a staggered manner in cross-sectional view.
- Refrigerant flows inside the porous flat tubes 2, and the fins 1 are provided perpendicular to the axial directions of the porous flat tubes 2.
- the porous flat tubes 2 and the fins 1 are formed of a highly conductive metal such as copper and aluminum, and are joined by methods such as brazing, soldering, and welding under a state in which the porous flat tubes 2 are inserted into heat transfer tube insertion parts, which are cut out on the fins 1, to transfer heat to each other.
- the fin 1 is configured of a first fin 1a arranged on the windward side of the flow direction of air, which is a heat-exchange fluid, and a second fin 1 b arranged on the leeward side.
- a single path of the porous flat tubes 2 is formed of four porous flat tubes 2a, 2b, 2c, and 2d as one unit.
- the porous flat tubes 2a and 2b penetrate the first fins 1 a arranged on the windward side of the flow direction of air, and form a first column.
- the porous flat tubes 2c and 2d penetrate the second fins 1 b arranged on the leeward side of the flow direction of air, and form a second column.
- multiple steps of the porous flat tubes 2a and 2b are arranged layeredly in the axial direction of the header 4 while penetrating the first fins 1a.
- multiple steps of the porous flat tubes 2c and 2d are arranged layeredly in the axial direction of the header 4 while penetrating the second fins 1 b.
- the header 4 has a hollow structure having a substantially rectangular cross section, and includes a refrigerant flow path therein.
- the refrigerant flow path is formed as a column bridging portion 5, which connects the porous flat tubes 2b and 2c in the column-wise direction.
- the other end part of the porous flat tube 2b is connected to the header 4, and the refrigerant having flowed out of the porous flat tube 2b passes through the column bridging portion 5 of the header 4 to move from column to column, and flows into one end part of the porous flat tube 2c of the second column.
- the refrigerant having flowed into one end part of the porous flat tube 2c passes through the U-bend 9 from the other end part of the porous flat tube 2c to move from step to step, and flows into one end part of the porous flat tube 2d. Then, the refrigerant flows out of the other end part of the porous flat tube 2d.
- gas refrigerant flows in from the other end part of the porous flat tube 2d of the second column, follows through a flow path opposite to that of the case in which the heat exchanger is used as the evaporator, and flows out of one end part of the porous flat tube 2a of the first column.
- the heat exchanger is configured by layering multiple steps of the paths of a unit formed in this manner, in the axial direction of the header 4.
- Fig. 3 is a cross-sectional view of the column bridging portion 5 when the heat exchanger according to Embodiment 1 is used as an evaporator.
- the column bridging portion 5 is formed as a substantially cuboidal hollow part inside the header 4.
- the porous flat tube 2b and the porous flat tube 2c are connected to and open to the column bridging portion 5, and two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b of the first column passes through the column bridging portion 5 to move between columns of the porous flat tubes 2b and 2c, and flows into one end part of the porous flat tube 2c of the second column.
- FIG. 3 The positional relation between the porous flat tube 2b and the porous flat tube 2c is shown in Fig. 3 , where the porous flat tube 2c of the second column is shifted from the porous flat tube 2b of the first column in the axial direction of the header 4.
- a refrigerant partition plate 7 horizontally partitioning the inside of the column bridging portion 5 is installed between the porous flat tube 2b and the porous flat tube 2c in the axial direction of the header 4.
- the refrigerant partition plate 7 is supported by straddling and being attached to two surfaces, which are a side wall of the column bridging portion 5 on which the porous flat tube 2b and the porous flat tube 2c open, and another side wall opposite to this side wall. Moreover, the refrigerant partition plate 7 is provided in the center position of the column-wise direction in which the porous flat tube 2b and the porous flat tube 2c are arranged, thus a first opening 7a is formed below the porous flat tube 2b, and a second opening 7b is formed above the porous flat tube 2c in the configuration.
- the refrigerant partition plate 7 configured in this manner blocks the shortest route for the two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b of the first column to flow into one end part of the porous flat tube 2c of the second column, and divides the flow path of the refrigerant into two parts.
- liquid refrigerant 6 in the two-phase gas-liquid refrigerant flows into the porous flat tube 2c through two flow paths, on the windward side and leeward side of the flow direction of heat-exchange fluid inside the column bridging portion 5, supplying the liquid refrigerant 6 evenly to the refrigerant flow paths of the porous flat tube 2c.
- the refrigerant partition plate 7 may be any form as long as it can obstruct the flow of the refrigerant, and may be a fine mesh plate or a protrusion formed on a side wall of the column bridging portion 5, for example.
- the refrigerant partition plate 7 may be formed integrally with the header 4, or may be attached as a separate body.
- the refrigerant partition plate is preferred to be made of the same material as that of the header 4, and may be made of a copper plate, an aluminum plate, or a resin plate, for example.
- Fig. 4 is a cross-sectional view of the column bridging portion 5 when the heat exchanger according to Embodiment 1 is used as a condenser.
- the flow direction of refrigerant flowing through the porous flat tube 2 of the heat exchanger is opposite to that of the case in which the heat exchanger is used as the evaporator described above.
- the refrigerant partition plate 7 blocks the shortest route for the refrigerant having flowed out of the porous flat tube 2c of the second column to flow into one end part of the porous flat tube 2b of the first column, and divides the flow path of the refrigerant into two parts.
- the liquid refrigerant 6 flows into the porous flat tube 2b through two flow paths, on the windward side and leeward side of the flow direction of heat-exchange fluid inside the column bridging portion 5, supplying gas refrigerant and the liquid refrigerant 6 evenly to the refrigerant flow paths of the porous flat tube 2b.
- gas refrigerant and the liquid refrigerant 6 flow evenly into the refrigerant flow paths of the porous flat tube 2b and the gas refrigerant is condensed, causing the condense effect to occur evenly in the refrigerant flow paths, and improving heat exchange performance as a condenser.
- Fig. 5 is a cross-sectional view of a column bridging portion 5 when a heat exchanger according to Embodiment 2 is used as an evaporator.
- the column bridging portion 5 is formed inside a header 4, as a hollow part having a substantially parallelogram-shaped cross section.
- a porous flat tube 2b and a porous flat tube 2c are connected to and open to the column bridging portion 5, and two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b of a first column passes through the column bridging portion 5 to move between columns of the porous flat tubes 2b and 2c, and flows into one end part of the porous flat tube 2c of a second column.
- FIG. 5 The positional relation between the porous flat tube 2b and the porous flat tube 2c is shown in Fig. 5 , where the porous flat tube 2b of the first column is provided in the vicinity of the upper side of the column bridging portion 5, and the porous flat tube 2c of the second column is provided in the vicinity of the lower side of the column bridging portion 5.
- first refrigerant partition plate 8a and a second refrigerant partition plate 8b horizontally partitioning the inside of the column bridging portion 5 are installed around the porous flat tube 2b and around the porous flat tube 2c.
- the first refrigerant partition plate 8a and the second refrigerant partition plate 8b are supported by straddling and being attached to two surfaces, which are a side wall of the column bridging portion 5 on which the porous flat tube 2b and the porous flat tube 2c open, and another side wall opposite to this side wall.
- the first refrigerant partition plate 8a surrounds the porous flat tube 2b, and has a first opening 8c opened downward on the windward side of the flow direction of heat-exchange fluid inside the column bridging portion 5. Meanwhile, the second refrigerant partition plate 8b surrounds the porous flat tube 2c, and has a second opening 8d opened upward on the leeward side of the flow direction of heat-exchange fluid inside the column bridging portion 5.
- the first refrigerant partition plate 8a and the second refrigerant partition plate 8b configured in this manner block the shortest route for two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b of the first column to flow into one end part of the porous flat tube 2c of the second column, and form the flow path for a refrigerant flow 3 inside the column bridging portion 5 into an S shape.
- liquid refrigerant 6 in the two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2b flows into the periphery of the porous flat tube 2c through the second opening 8d of the second refrigerant partition plate 8b, concentrates on the windward side of the flow direction of heat-exchange fluid, which is the deepest part of the second refrigerant partition plate 8b, and forms a pool of liquid.
- heat load is high on the windward side of the porous flat tube 2c, and thus supplying more liquid refrigerant thereto improves performance of the heat exchanger.
- the configuration of the above-mentioned heat exchanger allows the amount of liquid refrigerant on the windward side of the porous flat tube 2c to become relatively larger than that on the leeward side, improving performance of the heat exchanger.
- Fig. 6 is a cross-sectional view of the column bridging portion 5 when the heat exchanger according to Embodiment 2 is used as a condenser.
- the flow direction of refrigerant flowing through the porous flat tube 2 of the heat exchanger is opposite to that of the case in which the heat exchanger is used as the evaporator described above.
- the first refrigerant partition plate 8a and the second refrigerant partition plate 8b block the shortest route for the two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2c of the second column to flow into one end part of the porous flat tube 2b of the first column, and form the refrigerant flow 3 inside the column bridging portion 5 into an S shape.
- the liquid refrigerant 6 in the two-phase gas-liquid refrigerant having flowed out of the porous flat tube 2c flows into the periphery of the porous flat tube 2b through the first opening 8c of the first refrigerant partition plate 8a, concentrates on the leeward side of the flow direction of heat-exchange fluid, which is the deepest part of the first refrigerant partition plate 8a, and flows into the porous flat tube 2b.
- heat load is high on the windward side of the porous flat tube 2b, and thus supplying more gas refrigerant thereto improves performance of the heat exchanger.
- the configuration of the above-mentioned heat exchanger allows the amount of gas refrigerant on the windward side of the porous flat tube 2b to become relatively larger than that on the leeward side, improving performance of the heat exchanger.
- Fig. 7 is a refrigerant circuit diagram of an air-conditioning and refrigerating apparatus using the heat exchangers according to Embodiments 1 and 2.
- a refrigerant circuit shown in Fig. 7 includes a compressor 33, a condensing heat exchanger 34, an expansion device 35, an evaporative heat exchanger 36, and fans 37 driven by fan motors 38.
- a highly energy efficient air-conditioning and refrigerating apparatus can be implemented, by using the aforementioned heat exchanger according to Embodiments 1 and 2 as the condensing heat exchanger 34, the evaporative heat exchanger 36, or both.
- Heating energy efficiency capacity of indoor heat exchanger condenser / all input
- Cooling energy efficiency capacity of indoor heat exchanger evaporator / all input
- working fluids other gases, liquids, or gas-liquid mixture fluids may be adopted as working fluids.
- any refrigerating machine oils can be used regardless of whether they are miscible or immiscible, such as those based on mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorinated oil, in the heat exchangers described in the above Embodiments 1 and 2, and in the air-conditioning and refrigerating apparatus using the heat exchanger.
- header 4 of the heat exchanger arranged so that its axial direction is parallel to the gravity direction has been used as an example, the axial direction may be arranged parallel to the horizontal direction.
- the heat exchanger functions as a condenser
- adopting the structure of the header 4 according to Embodiment 1 or 2 allows gas refrigerant and the liquid refrigerant 6 to flow evenly into the refrigerant flow paths of the porous flat tube 2b, improving heat exchange performance as a condenser.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2013/076298 WO2015045105A1 (ja) | 2013-09-27 | 2013-09-27 | 熱交換器及びそれを用いた空気調和機 |
PCT/JP2014/075328 WO2015046275A1 (ja) | 2013-09-27 | 2014-09-24 | 熱交換器及びそれを用いた空気調和機 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP3051244A1 true EP3051244A1 (de) | 2016-08-03 |
EP3051244A4 EP3051244A4 (de) | 2017-05-24 |
EP3051244B1 EP3051244B1 (de) | 2018-12-19 |
Family
ID=52742309
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14847978.5A Active EP3051244B1 (de) | 2013-09-27 | 2014-09-24 | Wärmetauscher und klimaanlage damit |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3051244B1 (de) |
JP (1) | JP6120978B2 (de) |
WO (2) | WO2015045105A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10436514B2 (en) | 2015-12-21 | 2019-10-08 | Mitsubishi Electric Corporation | Heat exchanger and refrigeration cycle apparatus |
US11105538B2 (en) | 2015-12-01 | 2021-08-31 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
EP4235058A4 (de) * | 2020-10-20 | 2024-01-10 | Mitsubishi Electric Corp | Wärmetauscher und kältekreislaufvorrichtung |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7078840B2 (ja) * | 2018-01-19 | 2022-06-01 | ダイキン工業株式会社 | 熱交換器および空気調和装置 |
JP6806187B2 (ja) * | 2019-06-13 | 2021-01-06 | ダイキン工業株式会社 | 熱交換器 |
JPWO2023032155A1 (de) * | 2021-09-03 | 2023-03-09 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2733899A (en) * | 1956-02-07 | Lehmann | ||
JPH0749249Y2 (ja) * | 1988-11-10 | 1995-11-13 | 三菱重工業株式会社 | 熱交換器 |
JPH06117783A (ja) * | 1992-10-01 | 1994-04-28 | Showa Alum Corp | 積層型熱交換器 |
JPH06213532A (ja) * | 1993-01-20 | 1994-08-02 | Showa Alum Corp | 積層型熱交換器 |
JP4143955B2 (ja) * | 2001-11-30 | 2008-09-03 | 株式会社ティラド | 熱交換器 |
JP4055449B2 (ja) | 2002-03-27 | 2008-03-05 | 三菱電機株式会社 | 熱交換器およびこれを用いた空気調和機 |
JP2003302183A (ja) * | 2002-04-09 | 2003-10-24 | Toyo Radiator Co Ltd | 空調用熱交換器 |
JP3736514B2 (ja) * | 2002-09-13 | 2006-01-18 | 三菱電機株式会社 | 熱交換器および熱交換器を用いた空気調和機 |
JP2006029653A (ja) * | 2004-07-14 | 2006-02-02 | Calsonic Kansei Corp | 熱交換器 |
SE528412C2 (sv) * | 2005-03-15 | 2006-11-07 | Scania Cv Ab | Kylanordning där en första tank är försedd med yttre ytförstorande element och ett inre földesledande element |
JP2007032993A (ja) * | 2005-07-29 | 2007-02-08 | Showa Denko Kk | 熱交換器 |
-
2013
- 2013-09-27 WO PCT/JP2013/076298 patent/WO2015045105A1/ja active Application Filing
-
2014
- 2014-09-24 JP JP2015539281A patent/JP6120978B2/ja active Active
- 2014-09-24 WO PCT/JP2014/075328 patent/WO2015046275A1/ja active Application Filing
- 2014-09-24 EP EP14847978.5A patent/EP3051244B1/de active Active
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11105538B2 (en) | 2015-12-01 | 2021-08-31 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
US10436514B2 (en) | 2015-12-21 | 2019-10-08 | Mitsubishi Electric Corporation | Heat exchanger and refrigeration cycle apparatus |
EP4235058A4 (de) * | 2020-10-20 | 2024-01-10 | Mitsubishi Electric Corp | Wärmetauscher und kältekreislaufvorrichtung |
Also Published As
Publication number | Publication date |
---|---|
WO2015046275A1 (ja) | 2015-04-02 |
EP3051244A4 (de) | 2017-05-24 |
EP3051244B1 (de) | 2018-12-19 |
JP6120978B2 (ja) | 2017-04-26 |
WO2015045105A1 (ja) | 2015-04-02 |
JPWO2015046275A1 (ja) | 2017-03-09 |
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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 |
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