EP3156752A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- EP3156752A1 EP3156752A1 EP14894720.3A EP14894720A EP3156752A1 EP 3156752 A1 EP3156752 A1 EP 3156752A1 EP 14894720 A EP14894720 A EP 14894720A EP 3156752 A1 EP3156752 A1 EP 3156752A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- refrigerant
- transfer pipes
- heat transfer
- fins
- 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 62
- 238000010438 heat treatment Methods 0.000 claims description 12
- 238000010257 thawing Methods 0.000 claims description 10
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 15
- 239000007788 liquid Substances 0.000 description 13
- 238000001816 cooling Methods 0.000 description 10
- 238000010586 diagram Methods 0.000 description 9
- 230000005484 gravity Effects 0.000 description 8
- 230000004048 modification Effects 0.000 description 8
- 238000012986 modification Methods 0.000 description 8
- 238000005192 partition Methods 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000002844 melting Methods 0.000 description 1
- 230000008018 melting Effects 0.000 description 1
- 238000011176 pooling Methods 0.000 description 1
- 238000007665 sagging Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- 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
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
-
- 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
-
- 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
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
- F28D1/0435—Combination of units extending one behind the other
-
- 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
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape
Definitions
- the present invention relates to a heat exchanger in which lower ends of a plurality of heat transfer pipes disposed in parallel with spaces therebetween and extending in a vertical direction are connected by a distribution header for distributing a refrigerant.
- a heat exchanger tube that has a plurality of flat pipes that are disposed in a traverse direction with spaces therebetween in such a manner that the width direction thereof faces a front-back direction, corrugated fins that are disposed between the respective adjacent flat pipes, and a distribution header that is connected to the lower end of each flat pipe so as to communicate with the flat pipe and distributes a refrigerant, wherein heat exchange takes place between the refrigerant circulating through the flat pipes and air caused to circulate through the corrugated fins by the rotation of a fan (see PTL 1, for example).
- a problem that the heat exchanger described above faces is that, in a case where frost formed on the flat pipes and corrugated fins flows down to the top surfaces of the distribution headers, the overall circular arc cross-sectional shape of this top surface where the middle portion thereof in the front-back direction is the highest portion and the sides of the same sag gradually from the highest portion toward the front and back, causes the drops of water flowing along the arc and the direction of the wind to confront each other, making it impossible to drain the water smoothly from the distribution headers.
- the present invention aims to solve such problem and an object thereof is to provide a heat exchanger that has a simple structure and the improved drainage capability of the distribution header and thereby prevents frosting.
- a heat exchanger according to the present invention has:
- each distribution header is inclined downward from the windward side to the leeward side, gravity and the force of the wind can facilitate downward flow of drops of water on the top surface, improving the drainage capability of the distribution headers and anti-frosting performance of the distribution headers themselves.
- Fig. 1 is a circuit diagram showing an air conditioner 51 incorporated with a heat exchanger 1 according to Embodiment 1.
- Fig. 1 the solid arrows each show how a refrigerant flows during a cooling operation, the dotted lines each show how the refrigerant flows during a heating operation, and the chain arrows each show how the refrigerant flows during a defrosting operation.
- the air conditioner 51 has a compressor 52, a four-way valve 53 connected to the compressor 52 by a first solenoid valve 60A, a throttle device 55 connected by a first solenoid valve 60C, a heat source-side heat exchanger 54 connected to the four-way valve 53 by a first solenoid valve 60B, the throttle device 55 connected to the heat source-side heat exchanger 54 by the first solenoid valve 60C, and a load-side heat exchanger 56 having one side connected to the throttle device 55 and the other side connected to the four-way valve 53.
- the air conditioner 51 also has a heat source-side fan 57 facing the heat source-side heat exchanger 54, a load-side fan 58 facing the load-side heat exchanger 56, a second solenoid valve 61, and a controller 59.
- the compressor 52, four-way valve 53, heat source-side heat exchanger 54, throttle device 55, and load-side heat exchanger 56 are connected to one another by refrigerant piping, configuring a refrigerant circulation circuit.
- the compressor 52, four-way valve 53, throttle device 55, heat source-side fan 57, load-side fan 58, first solenoid valves 60A to C, second solenoid valve 61, and various other sensors are connected to the controller 59.
- the controller 59 switches a flow channel of the four-way valve 53, thereby switching between the cooling operation and the heating operation.
- the heat source-side heat exchanger 54 acts as a condenser in the cooling operation and as an evaporator in the heating operation.
- the load-side heat exchanger 56 acts as an evaporator in the cooling operation and as a condenser in the heating operation.
- the first solenoid valves 60A to C are opened during the cooling operation and the heating operation but are closed during the defrosting operation.
- the second solenoid valve 61 is closed during the cooling operation and the heating operation but is opened during the defrosting operation.
- the refrigerant in a state of a high pressure and high temperature gas that is discharged from the compressor 52 flows into the heat source-side heat exchanger 54 through the first solenoid valve 60A, four-way valve 53 and first solenoid valve 60B, turns into a high-pressure liquid refrigerant by being condensed through heat exchange with outside air supplied by the heat source-side fan 57, and flows out of the heat source-side heat exchanger 54.
- the low-pressure gaseous refrigerant that flows out of the load-side heat exchanger 56 is suctioned by the compressor 52 through the four-way valve 53.
- the refrigerant in a state of a high pressure and high temperature gas that is discharged from the compressor 52 flows into the load-side heat exchanger 56 through the first solenoid valve 60A and four-way valve 53, turns into a high-pressure liquid refrigerant by being condensed through heat exchange with the indoor air supplied by the load-side fan 58, and flows out of the load-side heat exchanger 56.
- the high-pressure liquid refrigerant that flows out of the load-side heat exchanger 56 flows into the throttle device 55 and becomes a low-pressure gas-liquid two-phase refrigerant.
- the low-pressure gas-liquid two-phase refrigerant that flows out of the throttle device 55 flows into the heat source-side heat exchanger 54 through the first solenoid valve 60C, turns into a low-pressure gaseous refrigerant by being vaporized through heat exchange with the outside air supplied by the heat source-side fan 57, and flows out of the heat source-side heat exchanger 54.
- the low-pressure gaseous refrigerant that flows out of the heat source-side heat exchanger 54 is suctioned by the compressor 52 through the first solenoid valve 60B and four-way valve 53.
- the refrigerant in a state of a high pressure and high temperature gas that is discharged from the compressor 52 flows into the heat source-side heat exchanger 54 through the second solenoid valve 61, turns into a gas-liquid two-phase or gaseous refrigerant by being subjected to heat exchange while melting frost adhering to the heat source-side heat exchanger 54, and flows out of the heat source-side heat exchanger 54.
- the high-pressure gas-liquid two-phase or gaseous refrigerant that flows out of the heat source-side heat exchanger 54 flows into the throttle device 55 and becomes a low-pressure gas-liquid two-phase or gaseous refrigerant.
- the low-pressure gas-liquid two-phase or gaseous refrigerant that flows out of the throttle device 55 passes through the load-side heat exchanger 56.
- the low-pressure gas-liquid two-phase or gaseous refrigerant that passes through the load-side heat exchanger 56 is suctioned by the compressor 52 through the four-way valve 53.
- the air conditioner performs defrosting in the direction of the flow of the refrigeration in the cooling operation, and thus it takes a while to defrost a section where frost grows.
- the high-temperature gas can be caused to flow from the section where frost grows, improving the defrosting efficiency and consequently reducing the defrosting time.
- Fig. 2 is a diagram in which the heat exchanger 1 according to Embodiment 1 of the present invention, which is the heat source-side heat exchanger 54 shown in Fig. 1 , is viewed from the windward side.
- Fig. 3 is a perspective view of main portions, showing the heat exchanger 1 shown in Fig. 2 .
- Fig. 4 is a diagram showing internal configurations of distribution headers 2, 7 shown in Fig. 3 .
- Fig. 5 is a flat cross-sectional diagram showing a folded-back header shown in Fig. 2 . Note that Fig. 3 only shows corrugated fins 5 held between a pair of flat pipes 4 and corrugated fins 5 held between a pair of flat pipes 6 and does not show the other flat pipes 4, 6 and corrugated fins 5 that are arranged in parallel.
- This heat exchanger 1 has a first distribution header 2 that is disposed in a direction perpendicular to the direction of the wind shown by the arrow C when seen in the vertical direction, a second distribution header 7 provided in parallel with the first distribution header 2, a plurality of first flat pipes 4, which are first heat transfer pipes that have lower ends connected to the first distribution header 2, have upper ends extending vertically, and are disposed at equal intervals, a folded-back header 3 that is provided in such a manner as to face the first distribution header 2 and the second distribution header 7 and has an upper portion of each of the first flat pipes 4 connected thereto, a plurality of second flat pipes 6, which are second heat transfer pipes that have upper ends connected to this folded-back header 3, have lower ends connected to the second distribution header 7, and are disposed at equal intervals, and the corrugated fins 5 that are provided in an air duct between the first flat pipes 4 adjacent to each other and an air duct between the second flat pipes 6 adjacent to each other.
- the first distribution header 2 and the second distribution header 7 are in the same shape and have a rectangular cross section.
- the first distribution header 2 has a refrigerant inflow portion 2A extending in a horizontal direction, to which the refrigerant flows in.
- the refrigerant piping is connected to this refrigerant inflow portion 2A.
- the first distribution header 2 is also provided with a distribution pipe 2B that extends internally in the horizontal direction. A tip end of the refrigerant inflow portion 2A is connected vertically to this distribution pipe 2B.
- the hollow second distribution header 7 has a refrigerant outflow portion 7A extending in the horizontal direction, of which the refrigerant flows out.
- the refrigerant piping is connected to this refrigerant outflow portion 7A.
- a plurality of holes into which the lower ends of the first flat pipes 4 are inserted are formed in the first distribution header 2.
- a plurality of holes into which the lower ends of the second flat pipes 6 are inserted are formed in the second distribution header 7.
- the first distribution header 2 and the second distribution header 7 have, respectively, inclined surfaces 10, 11 having top surfaces thereof inclined downward from the windward side to the leeward side.
- the starting points of the inclined surfaces 10, 11 are located higher than upper connecting points of the first flat pipes 4 extending vertically from the first distribution header 2.
- a partition plate may be provided on the inside of each of the distribution headers 2, 7 in order to adjust the distribution ratio of each of the first and second flat pipes 4, 6.
- first flat pipes 4 and second flat pipes 6 Holes into which the upper ends of the first flat pipes 4 and second flat pipes 6 are inserted are formed in the folded-back header 3.
- the first flat pipes 4 and the second flat pipes 6 face each other in a longitudinal direction.
- a partition wall 8 is provided between a pair of first and second flat pipes 4 and 6 and a pair of first and second flat pipes 4 and 6 adjacent thereto. This partition wall 8 regulates the refrigerant to flow in the direction of the arrow A shown in Fig. 5 .
- the first distribution header 2, folded-back header 3, second distribution header 7, first flat pipes 4, second flat pipes 6, corrugated fins 5, and distribution pipe 2B are made of, for example, aluminum.
- the refrigerant inflow portion 2A and the refrigerant outflow portion 7A may be provided in plurality.
- the first flat pipes 4 and the second flat pipes 6 are flat pipes that internally have a plurality of flow channels 4a, 6a extending individually in the vertical direction.
- the longitudinal direction of these rectangular first flat pipes 4 and second flat pipes 6 are the vertical direction, and the short direction thereof are positioned along the direction of the wind.
- the corrugated fins 5 and the first flat pipes 4 are preferably joined together by brazing, as well as the corrugated fins 5 and the second flat pipes 6. It should be noted that, needless to say, the number of first flat pipes 4 and the number of second flat pipes 6 are not limited to the numbers shown in Fig. 2 .
- the refrigerant flowing through the refrigerant piping flows into the first distribution header 2 through the refrigerant inflow portion 2A, is then distributed, and then flows upward through each of the flow channels 4a of the plurality of first flat pipes 4 from the lower ends of the first flat pipes 4. While flowing through the first flat pipes 4, this refrigerant is subjected to heat exchange with air that is circulated through the corrugated fins 5 by the fans.
- the refrigerant that is circulated through the first flat pipes 4 reaches the folded-back header 3, turns back at the folded-back header 3, and flows down each of the flow channels 6a of the second flat pipes 6. While flowing through the first flat pipes 4, this refrigerant is subjected to heat exchange with air that is circulated through the corrugated fins 5 by the fans.
- the refrigerant that flows down each of the second flat pipes 6 joins at the second distribution header 7 and flows out to the refrigerant piping through the refrigerant outflow portion 7A.
- the direction of the flow of the refrigerant can be reversed.
- Fig. 7 is a perspective view of main portions, showing a modification of the heat exchanger 1 according to Embodiment 1 of the present invention.
- the inclined surfaces 10, 11 are in the shape of an arc, sagging from the windward side to the leeward side.
- the starting point of the inclined surface 10 is located higher than the upper connecting points of the first flat pipes 4 extending vertically from the first distribution header 2.
- the starting point of the inclined surface 11 is located higher than the upper connecting points of the second flat pipes 6 extending vertically from the second distribution header 7.
- the drops of water 12 drained into the first distribution header 2 and the second distribution header 7 flow in the direction of gravity due to the inclination of the inclined surfaces 10, 11.
- the inclined surfaces 10, 11 at the top surfaces of the distribution headers 2, 7 have a streamlined shape, the wind flowing through the heat exchanger 1 flows along the distribution headers 2, 7 more as compared to a linear-shaped inclined surface, and thus, the gravity and the force of the wind facilitate the flow of the drops of water 12.
- Fig. 8 is a perspective view of main portions, showing another modification of the heat exchanger 1 according to Embodiment 1 of the present invention.
- the inclined surfaces 10, 11 at the top surfaces are in the same shape as those shown in Fig. 3 ; however this modification is different from Embodiment 1 in that the surface of the first distribution header 2 and the surface of the second distribution header 7 that face each other have inclined surfaces 13, 14, respectively, which are configured such that a distance therebetween increases as the inclined surfaces 13, 14 incline downward.
- each first distribution header 2 and each second distribution header 7 needs to be reduced due to limitations in installation space.
- the first distribution header 2 and the second distribution header 7 have, on the surfaces thereof facing each other, the inclined surfaces 13, 14 that are inclined vertically, wherein the distance between the inclined surfaces 13, 14 increases gradually toward the lower side thereof.
- the drops of water 12 do not bridge the space between the first distribution header 2 and the second distribution header 7 easily, improving anti-frosting performance of the first distribution header 2 and the second distribution header 7.
- Fig. 10 is a perspective view showing main portions of a heat exchanger according to Embodiment 2 of the present invention.
- front edge portions of the corrugated fins 5 protrude toward the windward side from the windward end surfaces of the first flat pipes 4 and second flat pipes 6.
- corrugated fins 5 are inclined gradually downward from the windward side toward the leeward side.
- the downward inclination of the corrugated fins 5 from the windward side to the leeward side enables drainage of water using both the gravity and the force of the wind, further improving the drainage capability of the corrugated fins 5.
- Fig. 11 is a side view showing main portions of a heat exchanger 1 according to Embodiment 3 of the present invention.
- the both sides of the fins 5 are brazed by the flat pipes 4, 6 at joint portions 15 and inclined downward from the windward side to the leeward side.
- drainage grooves 9, which are inclined along the joint portions 15 between the flat pipes 4, 6 and the corrugated fins 5 and extend linearly, are formed in the flat pipes 4, 6.
- drops of water 12 are transferred from the corrugated fins 5 to the first flat pipes 4 and the second flat pipes 6 and pool in the drainage grooves 9 due to gravity.
- the drops of water 12 pooling in the drainage grooves 9 are pushed out by both the gravity and the force of the wind, improving the drainage capability of the first flat pipes 4 and second flat pipes 6.
- the heat exchanger is used in the air conditioner; however, needless to say, the applications of the heat exchanger are not limited to an air conditioner.
- the heat exchanger may be used in other refrigeration cycle devices having a refrigerant circulation circuit.
- corrugated fins 5 are merely an example; thus, the shape of the fins does not have to be corrugated.
- the first flat pipes 4 and the second flat pipes 6, too, are merely an example; thus, the shape of the pipes does not have to be flat.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
- The present invention relates to a heat exchanger in which lower ends of a plurality of heat transfer pipes disposed in parallel with spaces therebetween and extending in a vertical direction are connected by a distribution header for distributing a refrigerant.
- There has conventionally been known a heat exchanger tube that has a plurality of flat pipes that are disposed in a traverse direction with spaces therebetween in such a manner that the width direction thereof faces a front-back direction, corrugated fins that are disposed between the respective adjacent flat pipes, and a distribution header that is connected to the lower end of each flat pipe so as to communicate with the flat pipe and distributes a refrigerant, wherein heat exchange takes place between the refrigerant circulating through the flat pipes and air caused to circulate through the corrugated fins by the rotation of a fan (see
PTL 1, for example). - [PTL 1] Japanese Patent Application Laid-Open No.
2006-170601 Fig. 1 ) - A problem that the heat exchanger described above faces is that, in a case where frost formed on the flat pipes and corrugated fins flows down to the top surfaces of the distribution headers, the overall circular arc cross-sectional shape of this top surface where the middle portion thereof in the front-back direction is the highest portion and the sides of the same sag gradually from the highest portion toward the front and back, causes the drops of water flowing along the arc and the direction of the wind to confront each other, making it impossible to drain the water smoothly from the distribution headers.
- The present invention aims to solve such problem and an object thereof is to provide a heat exchanger that has a simple structure and the improved drainage capability of the distribution header and thereby prevents frosting.
- A heat exchanger according to the present invention has:
- a plurality of heat transfer pipes that are disposed in parallel with spaces therebetween;
- distribution headers that are respectively connected to each of lower ends of the plurality of heat transfer pipes so as to communicate with the heat transfer pipes and distributes a refrigerant; and
- a plurality of fins that are provided in an air duct between the heat transfer pipes adjacent to each other,
- wherein the distribution headers have upper surfaces inclined downward from a windward side to a leeward side.
- According to the heat exchanger of the present invention, because the top surface of each distribution header is inclined downward from the windward side to the leeward side, gravity and the force of the wind can facilitate downward flow of drops of water on the top surface, improving the drainage capability of the distribution headers and anti-frosting performance of the distribution headers themselves.
-
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Fig. 1 is a circuit diagram showing an air conditioner incorporated with a heat exchanger according toEmbodiment 1 of the present invention. -
Fig. 2 is a diagram in which the heat exchanger according toEmbodiment 1 of the present invention is viewed from the windward side. -
Fig. 3 is a perspective view of main portions, showing the heat exchanger shown inFig. 2 . -
Fig. 4 is a diagram showing an internal configuration of a distribution header shown inFig. 3 . -
Fig. 5 is a flat cross-sectional diagram showing a folded-back header shown inFig. 2 . -
Fig. 6 is a diagram showing a state of drops of water on the distribution header shown inFig. 3 . -
Fig. 7 is a perspective view of main portions, showing a modification of the heat exchanger according toEmbodiment 1 of the present invention. -
Fig. 8 is a perspective view of main portions, showing another modification of the heat exchanger according toEmbodiment 1 of the present invention. -
Fig. 9 is a side view of main portions, showing a behavior of drops of water in the heat exchanger shown inFig. 8 . -
Fig. 10 is a side view of main portions, showing a heat exchanger according toEmbodiment 2 of the present invention. -
Fig. 11 is a side view of main portions, showing a heat exchanger according toEmbodiment 3 of the present invention. - A heat exchanger according to each of the embodiments of the present invention is described hereinafter with reference to the drawings, wherein the same reference numerals are used to describe the same or relevant members and sections shown in the drawings.
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Fig. 1 is a circuit diagram showing anair conditioner 51 incorporated with aheat exchanger 1 according toEmbodiment 1. - In
Fig. 1 , the solid arrows each show how a refrigerant flows during a cooling operation, the dotted lines each show how the refrigerant flows during a heating operation, and the chain arrows each show how the refrigerant flows during a defrosting operation. - The
air conditioner 51 has acompressor 52, a four-way valve 53 connected to thecompressor 52 by afirst solenoid valve 60A, athrottle device 55 connected by afirst solenoid valve 60C, a heat source-side heat exchanger 54 connected to the four-way valve 53 by afirst solenoid valve 60B, thethrottle device 55 connected to the heat source-side heat exchanger 54 by thefirst solenoid valve 60C, and a load-side heat exchanger 56 having one side connected to thethrottle device 55 and the other side connected to the four-way valve 53. - The
air conditioner 51 also has a heat source-side fan 57 facing the heat source-side heat exchanger 54, a load-side fan 58 facing the load-side heat exchanger 56, asecond solenoid valve 61, and acontroller 59. - The
compressor 52, four-way valve 53, heat source-side heat exchanger 54,throttle device 55, and load-side heat exchanger 56 are connected to one another by refrigerant piping, configuring a refrigerant circulation circuit. - The
compressor 52, four-way valve 53,throttle device 55, heat source-side fan 57, load-side fan 58,first solenoid valves 60A to C,second solenoid valve 61, and various other sensors are connected to thecontroller 59. - The
controller 59 switches a flow channel of the four-way valve 53, thereby switching between the cooling operation and the heating operation. The heat source-side heat exchanger 54 acts as a condenser in the cooling operation and as an evaporator in the heating operation. - The load-
side heat exchanger 56 acts as an evaporator in the cooling operation and as a condenser in the heating operation. - The
first solenoid valves 60A to C are opened during the cooling operation and the heating operation but are closed during the defrosting operation. Thesecond solenoid valve 61 is closed during the cooling operation and the heating operation but is opened during the defrosting operation. - The flow of the refrigerant in the cooling operation of the
air conditioner 51 is described next. - The refrigerant in a state of a high pressure and high temperature gas that is discharged from the
compressor 52 flows into the heat source-side heat exchanger 54 through thefirst solenoid valve 60A, four-way valve 53 andfirst solenoid valve 60B, turns into a high-pressure liquid refrigerant by being condensed through heat exchange with outside air supplied by the heat source-side fan 57, and flows out of the heat source-side heat exchanger 54. - The refrigerant in a state of the high pressure liquid that flows out of the heat source-
side heat exchanger 54 flows into thethrottle device 55 through thefirst solenoid valve 60C and becomes a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant that flows out of thethrottle device 55 flows into the load-side heat exchanger 56, turns into a low-pressure gaseous refrigerant by being vaporized through heat exchange with indoor air supplied by the load-side fan 58, and flows out of the load-side heat exchanger 56. The low-pressure gaseous refrigerant that flows out of the load-side heat exchanger 56 is suctioned by thecompressor 52 through the four-way valve 53. - The flow of the refrigerant in the heating operation is described next.
- The refrigerant in a state of a high pressure and high temperature gas that is discharged from the
compressor 52 flows into the load-side heat exchanger 56 through thefirst solenoid valve 60A and four-way valve 53, turns into a high-pressure liquid refrigerant by being condensed through heat exchange with the indoor air supplied by the load-side fan 58, and flows out of the load-side heat exchanger 56. The high-pressure liquid refrigerant that flows out of the load-side heat exchanger 56 flows into thethrottle device 55 and becomes a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant that flows out of thethrottle device 55 flows into the heat source-side heat exchanger 54 through thefirst solenoid valve 60C, turns into a low-pressure gaseous refrigerant by being vaporized through heat exchange with the outside air supplied by the heat source-side fan 57, and flows out of the heat source-side heat exchanger 54. The low-pressure gaseous refrigerant that flows out of the heat source-side heat exchanger 54 is suctioned by thecompressor 52 through thefirst solenoid valve 60B and four-way valve 53. - The flow of the refrigerant in the defrosting operation is described next.
- The refrigerant in a state of a high pressure and high temperature gas that is discharged from the
compressor 52 flows into the heat source-side heat exchanger 54 through thesecond solenoid valve 61, turns into a gas-liquid two-phase or gaseous refrigerant by being subjected to heat exchange while melting frost adhering to the heat source-side heat exchanger 54, and flows out of the heat source-side heat exchanger 54. The high-pressure gas-liquid two-phase or gaseous refrigerant that flows out of the heat source-side heat exchanger 54 flows into thethrottle device 55 and becomes a low-pressure gas-liquid two-phase or gaseous refrigerant. The low-pressure gas-liquid two-phase or gaseous refrigerant that flows out of thethrottle device 55 passes through the load-side heat exchanger 56. The low-pressure gas-liquid two-phase or gaseous refrigerant that passes through the load-side heat exchanger 56 is suctioned by thecompressor 52 through the four-way valve 53. - Frost adheres gradually to the heat source-
side heat exchanger 54 and grows from the direction of the flow of the refrigerant in the heating operation. When defrosting, the air conditioner performs defrosting in the direction of the flow of the refrigeration in the cooling operation, and thus it takes a while to defrost a section where frost grows. However, by performing defrosting in the direction of the flow of the refrigeration in the heating operation as described above, the high-temperature gas can be caused to flow from the section where frost grows, improving the defrosting efficiency and consequently reducing the defrosting time. -
Fig. 2 is a diagram in which theheat exchanger 1 according toEmbodiment 1 of the present invention, which is the heat source-side heat exchanger 54 shown inFig. 1 , is viewed from the windward side.Fig. 3 is a perspective view of main portions, showing theheat exchanger 1 shown inFig. 2 .Fig. 4 is a diagram showing internal configurations ofdistribution headers Fig. 3 .Fig. 5 is a flat cross-sectional diagram showing a folded-back header shown inFig. 2 . Note thatFig. 3 only showscorrugated fins 5 held between a pair offlat pipes 4 andcorrugated fins 5 held between a pair offlat pipes 6 and does not show the otherflat pipes corrugated fins 5 that are arranged in parallel. - This
heat exchanger 1 has afirst distribution header 2 that is disposed in a direction perpendicular to the direction of the wind shown by the arrow C when seen in the vertical direction, asecond distribution header 7 provided in parallel with thefirst distribution header 2, a plurality of firstflat pipes 4, which are first heat transfer pipes that have lower ends connected to thefirst distribution header 2, have upper ends extending vertically, and are disposed at equal intervals, a folded-back header 3 that is provided in such a manner as to face thefirst distribution header 2 and thesecond distribution header 7 and has an upper portion of each of the firstflat pipes 4 connected thereto, a plurality of secondflat pipes 6, which are second heat transfer pipes that have upper ends connected to this folded-back header 3, have lower ends connected to thesecond distribution header 7, and are disposed at equal intervals, and thecorrugated fins 5 that are provided in an air duct between the firstflat pipes 4 adjacent to each other and an air duct between the secondflat pipes 6 adjacent to each other. - The
first distribution header 2 and thesecond distribution header 7 are in the same shape and have a rectangular cross section. - The
first distribution header 2 has arefrigerant inflow portion 2A extending in a horizontal direction, to which the refrigerant flows in. The refrigerant piping is connected to thisrefrigerant inflow portion 2A. Thefirst distribution header 2 is also provided with adistribution pipe 2B that extends internally in the horizontal direction. A tip end of therefrigerant inflow portion 2A is connected vertically to thisdistribution pipe 2B. - The hollow
second distribution header 7 has arefrigerant outflow portion 7A extending in the horizontal direction, of which the refrigerant flows out. The refrigerant piping is connected to thisrefrigerant outflow portion 7A. - A plurality of holes into which the lower ends of the first
flat pipes 4 are inserted are formed in thefirst distribution header 2. - A plurality of holes into which the lower ends of the second
flat pipes 6 are inserted are formed in thesecond distribution header 7. - The
first distribution header 2 and thesecond distribution header 7 have, respectively, inclined surfaces 10, 11 having top surfaces thereof inclined downward from the windward side to the leeward side. The starting points of theinclined surfaces flat pipes 4 extending vertically from thefirst distribution header 2. - Note that a partition plate may be provided on the inside of each of the
distribution headers flat pipes - Holes into which the upper ends of the first
flat pipes 4 and secondflat pipes 6 are inserted are formed in the folded-back header 3. The firstflat pipes 4 and the secondflat pipes 6 face each other in a longitudinal direction. Apartition wall 8 is provided between a pair of first and secondflat pipes flat pipes partition wall 8 regulates the refrigerant to flow in the direction of the arrow A shown inFig. 5 . - The
first distribution header 2, folded-back header 3,second distribution header 7, firstflat pipes 4, secondflat pipes 6,corrugated fins 5, anddistribution pipe 2B are made of, for example, aluminum. Therefrigerant inflow portion 2A and therefrigerant outflow portion 7A may be provided in plurality. - The first
flat pipes 4 and the secondflat pipes 6 are flat pipes that internally have a plurality offlow channels flat pipes 4 and secondflat pipes 6 are the vertical direction, and the short direction thereof are positioned along the direction of the wind. Thecorrugated fins 5 and the firstflat pipes 4 are preferably joined together by brazing, as well as thecorrugated fins 5 and the secondflat pipes 6. It should be noted that, needless to say, the number of firstflat pipes 4 and the number of secondflat pipes 6 are not limited to the numbers shown inFig. 2 . - The flow of the refrigerant in the
heat exchanger 1 is described next. - The refrigerant flowing through the refrigerant piping flows into the
first distribution header 2 through therefrigerant inflow portion 2A, is then distributed, and then flows upward through each of theflow channels 4a of the plurality of firstflat pipes 4 from the lower ends of the firstflat pipes 4. While flowing through the firstflat pipes 4, this refrigerant is subjected to heat exchange with air that is circulated through thecorrugated fins 5 by the fans. - The refrigerant that is circulated through the first
flat pipes 4 reaches the folded-back header 3, turns back at the folded-back header 3, and flows down each of theflow channels 6a of the secondflat pipes 6. While flowing through the firstflat pipes 4, this refrigerant is subjected to heat exchange with air that is circulated through thecorrugated fins 5 by the fans. - The refrigerant that flows down each of the second
flat pipes 6 joins at thesecond distribution header 7 and flows out to the refrigerant piping through therefrigerant outflow portion 7A. The direction of the flow of the refrigerant can be reversed. - The effects of the
heat exchanger 1 having the foregoing configuration are described next. - As shown in
Fig. 6 , drops ofwater 12 drained into thefirst distribution header 2 and thesecond distribution header 7 flow in the direction of gravity shown by the arrow B, due to theinclined surfaces first distribution header 2 and thesecond distribution header 7. The wind flowing through theheat exchanger 1 flows along theinclined surfaces distribution headers water 12. Consequently, the drainage capability improves, resulting in an improvement of anti-frosting performance of theheaders -
Fig. 7 is a perspective view of main portions, showing a modification of theheat exchanger 1 according toEmbodiment 1 of the present invention. - In this modification, the
inclined surfaces - The starting point of the
inclined surface 10 is located higher than the upper connecting points of the firstflat pipes 4 extending vertically from thefirst distribution header 2. The starting point of theinclined surface 11 is located higher than the upper connecting points of the secondflat pipes 6 extending vertically from thesecond distribution header 7. - The rest of the configuration is the same as that of the
heat exchanger 1 shown inFig. 3 . - In this modification, the drops of
water 12 drained into thefirst distribution header 2 and thesecond distribution header 7 flow in the direction of gravity due to the inclination of theinclined surfaces inclined surfaces distribution headers heat exchanger 1 flows along thedistribution headers water 12. - Consequently, the drainage capability of the
distribution headers -
Fig. 8 is a perspective view of main portions, showing another modification of theheat exchanger 1 according toEmbodiment 1 of the present invention. In this modification, theinclined surfaces Fig. 3 ; however this modification is different fromEmbodiment 1 in that the surface of thefirst distribution header 2 and the surface of thesecond distribution header 7 that face each other have inclinedsurfaces inclined surfaces - The rest of the configuration is the same as that of the
heat exchanger 1 shown inFig. 3 . - For example, when a plurality of
heat exchangers 1 are arranged in rows, in some cases the distance between eachfirst distribution header 2 and eachsecond distribution header 7 needs to be reduced due to limitations in installation space. - In such a case, the drops of
water 12 flowing down the top surfaces of thefirst distribution header 2 andsecond distribution header 7 bridge the space between thefirst distribution header 2 and thesecond distribution header 7 due to the surface tension, growing frost on the bridged section. - In order to cope with this situation, the
first distribution header 2 and thesecond distribution header 7 have, on the surfaces thereof facing each other, theinclined surfaces inclined surfaces - Accordingly, as shown in
Fig. 9 , the drops ofwater 12 do not bridge the space between thefirst distribution header 2 and thesecond distribution header 7 easily, improving anti-frosting performance of thefirst distribution header 2 and thesecond distribution header 7. -
Fig. 10 is a perspective view showing main portions of a heat exchanger according toEmbodiment 2 of the present invention. - In this embodiment, front edge portions of the
corrugated fins 5 protrude toward the windward side from the windward end surfaces of the firstflat pipes 4 and secondflat pipes 6. - Also, the
corrugated fins 5 are inclined gradually downward from the windward side toward the leeward side. - The rest of the configuration is the same as that of the
heat exchanger 1 ofEmbodiment 1. - In this embodiment, because the front edge portions of the
fins 5 protrude toward the windward side from the windward side of theflat pipes water 12 at the front edge portions of thecorrugated fins 5 drip without being transferred to theflat pipes corrugated fins 5. - In addition, the downward inclination of the
corrugated fins 5 from the windward side to the leeward side enables drainage of water using both the gravity and the force of the wind, further improving the drainage capability of thecorrugated fins 5. -
Fig. 11 is a side view showing main portions of aheat exchanger 1 according toEmbodiment 3 of the present invention. - In this embodiment, the both sides of the
fins 5 are brazed by theflat pipes joint portions 15 and inclined downward from the windward side to the leeward side. - Moreover, drainage grooves 9, which are inclined along the
joint portions 15 between theflat pipes corrugated fins 5 and extend linearly, are formed in theflat pipes - The rest of the configuration is the same as that of the
heat exchanger 1 ofEmbodiment 2. - In this embodiment, drops of
water 12 are transferred from thecorrugated fins 5 to the firstflat pipes 4 and the secondflat pipes 6 and pool in the drainage grooves 9 due to gravity. The drops ofwater 12 pooling in the drainage grooves 9 are pushed out by both the gravity and the force of the wind, improving the drainage capability of the firstflat pipes 4 and secondflat pipes 6. - Each of the foregoing embodiments has described a case where the heat exchanger is used in the air conditioner; however, needless to say, the applications of the heat exchanger are not limited to an air conditioner. For example, the heat exchanger may be used in other refrigeration cycle devices having a refrigerant circulation circuit.
- Each of the foregoing embodiments has also described the case where the air conditioner switches between the cooling operation and the heating operation; however, the present invention is not limited thereto and the air conditioner may perform either the cooling operation or the heating operation.
- The
corrugated fins 5 are merely an example; thus, the shape of the fins does not have to be corrugated. - The first
flat pipes 4 and the secondflat pipes 6, too, are merely an example; thus, the shape of the pipes does not have to be flat. -
- 1
- Heat exchanger
- 2
- First distribution header
- 2A
- Refrigerant inflow portion
- 2B
- Distribution pipe
- 3
- Folded-back header
- 4
- First flat pipe (first heat transfer pipe)
- 5
- Corrugated fin
- 6
- Second flat pipe (second heat transfer pipe)
- 7
- Second distribution header
- 7A
- Refrigerant outflow portion
- 8
- Partition wall
- 9
- Drainage groove
- 15
- Joint portion
- 51
- Air conditioner
- 52
- Compressor
- 53
- Four-way valve
- 54
- Heat source-side heat exchanger
- 55
- Throttle device
- 56
- Load-side heat exchanger
- 57
- Heat source-side fan
- 58
- Load-side fan
- 59
- Controller
- 60A to C
- First solenoid valve
- 61
- Second solenoid valve
Claims (9)
- A heat exchanger, comprising:a plurality of heat transfer pipes that are disposed in parallel with spaces therebetween;distribution headers that are respectively connected to lower ends of the plurality of heat transfer pipes so as to communicate with the heat transfer pipes and distribute a refrigerant; anda plurality of fins that are provided in an air duct between the heat transfer pipes adjacent to each other,wherein the distribution headers have top surfaces inclined downward from a windward side to a leeward side.
- The heat exchanger according to claim 1, wherein inclined surfaces, which are the inclined top surfaces, each have an arc shape protruding upward at a middle portion.
- The heat exchanger according to claim 1 or 2, wherein the distribution headers are arranged at least in two rows toward a direction of wind, and opposing surfaces thereof facing each other are inclined surfaces that are configured such that a distance therebetween increases toward a lower side.
- The heat exchanger according to any one of claims 1 to 3, wherein end surfaces of the fins on the windward side protrude toward the windward side from end surfaces of the heat transfer pipes on the windward side.
- The heat exchanger according to any one of claims 1 to 4, wherein the fins are provided to be inclined downward from the windward side to the leeward side.
- The heat exchanger according to any one of claims 1 to 5, wherein grooves that are inclined downward from the windward side to the leeward side are formed on surfaces of joint portions between the heat transfer pipes and the fins.
- The heat exchanger according to any one of claims 1 to 6, wherein the heat transfer pipes are flat pipes which have a plurality of flow channels, and the longitudinal direction of which is a vertical direction.
- The heat exchanger according to any one of claims 1 to 7, wherein the fins are corrugated fins.
- The heat exchanger according to any one of claims 1 to 8, wherein the heat exchanger is a heat source-side heat exchanger of an air conditioner, and a direction of flow of the refrigerant in the heat source-side heat exchanger is the same in both defrosting and heating.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2014/065766 WO2015189990A1 (en) | 2014-06-13 | 2014-06-13 | Heat exchanger |
Publications (3)
Publication Number | Publication Date |
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EP3156752A1 true EP3156752A1 (en) | 2017-04-19 |
EP3156752A4 EP3156752A4 (en) | 2018-02-21 |
EP3156752B1 EP3156752B1 (en) | 2020-11-11 |
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ID=54833117
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EP14894720.3A Active EP3156752B1 (en) | 2014-06-13 | 2014-06-13 | Heat exchanger |
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EP (1) | EP3156752B1 (en) |
JP (1) | JP6300915B2 (en) |
WO (1) | WO2015189990A1 (en) |
Cited By (2)
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CN112368536A (en) * | 2018-07-11 | 2021-02-12 | 三菱电机株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
EP3805651A4 (en) * | 2018-06-11 | 2021-06-16 | Mitsubishi Electric Corporation | Air conditioner outdoor unit and air conditioner |
Families Citing this family (6)
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JP2018155479A (en) * | 2017-03-16 | 2018-10-04 | ダイキン工業株式会社 | Heat exchanger having heat transfer pipe unit |
WO2018168759A1 (en) * | 2017-03-16 | 2018-09-20 | ダイキン工業株式会社 | Heat exchanger having heat transfer tube unit |
JP6717256B2 (en) * | 2017-05-10 | 2020-07-01 | 株式会社デンソー | Refrigerant evaporator and manufacturing method thereof |
JP6925393B2 (en) * | 2018-06-11 | 2021-08-25 | 三菱電機株式会社 | Outdoor unit of air conditioner and air conditioner |
JP7335690B2 (en) | 2018-11-07 | 2023-08-30 | ダイキン工業株式会社 | HEAT EXCHANGER AND HEAT EXCHANGER MANUFACTURING METHOD |
JP2023072100A (en) * | 2020-04-06 | 2023-05-24 | 三菱電機株式会社 | Heat exchanger, air conditioner equipped with heat exchanger, and manufacturing method of heat exchanger |
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JPS6189449A (en) * | 1984-10-05 | 1986-05-07 | 株式会社日立製作所 | Refrigeration cycle |
US4829780A (en) * | 1988-01-28 | 1989-05-16 | Modine Manufacturing Company | Evaporator with improved condensate collection |
JPH0552581U (en) * | 1991-12-09 | 1993-07-13 | 昭和アルミニウム株式会社 | Heat exchanger |
JPH07190661A (en) * | 1993-12-27 | 1995-07-28 | Hitachi Ltd | Heat exchanger |
JPH11108583A (en) * | 1997-10-08 | 1999-04-23 | Calsonic Corp | Evaporator |
JP3903866B2 (en) * | 2002-07-19 | 2007-04-11 | 株式会社デンソー | Cooler |
JP2006170601A (en) * | 2004-07-05 | 2006-06-29 | Showa Denko Kk | Evaporator |
JP2007232287A (en) * | 2006-03-01 | 2007-09-13 | Calsonic Kansei Corp | Heat exchanger and integral type heat exchanger |
JP5042927B2 (en) * | 2008-06-11 | 2012-10-03 | シャープ株式会社 | Heat exchanger |
KR101500751B1 (en) * | 2008-12-23 | 2015-03-09 | 두산인프라코어 주식회사 | Inner partition type oil cooler |
JP5270732B2 (en) * | 2011-09-05 | 2013-08-21 | シャープ株式会社 | Parallel flow type heat exchanger and air conditioner equipped with the same |
JP5907719B2 (en) * | 2011-12-19 | 2016-04-26 | 株式会社ケーヒン・サーマル・テクノロジー | Cooling unit for vehicle air conditioner |
-
2014
- 2014-06-13 WO PCT/JP2014/065766 patent/WO2015189990A1/en active Application Filing
- 2014-06-13 JP JP2016527597A patent/JP6300915B2/en active Active
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
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EP3805651A4 (en) * | 2018-06-11 | 2021-06-16 | Mitsubishi Electric Corporation | Air conditioner outdoor unit and air conditioner |
US11506402B2 (en) | 2018-06-11 | 2022-11-22 | Mitsubishi Electric Corporation | Outdoor unit of air-conditioning apparatus and air-conditioning apparatus |
EP4279850A3 (en) * | 2018-06-11 | 2024-03-06 | Mitsubishi Electric Corporation | Outdoor unit of air-conditioning apparatus and air-conditioning apparatus |
CN112368536A (en) * | 2018-07-11 | 2021-02-12 | 三菱电机株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
CN112368536B (en) * | 2018-07-11 | 2022-04-15 | 三菱电机株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
US11573056B2 (en) | 2018-07-11 | 2023-02-07 | Mitsubishi Electric Corporation | Heat exchanger, heat exchanger unit, and refrigeration cycle apparatus |
Also Published As
Publication number | Publication date |
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JP6300915B2 (en) | 2018-03-28 |
WO2015189990A1 (en) | 2015-12-17 |
JPWO2015189990A1 (en) | 2017-04-20 |
EP3156752B1 (en) | 2020-11-11 |
EP3156752A4 (en) | 2018-02-21 |
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