CN106403641A - Heat exchanger and refrigeration cycle apparatus - Google Patents
Heat exchanger and refrigeration cycle apparatus Download PDFInfo
- Publication number
- CN106403641A CN106403641A CN201610365863.8A CN201610365863A CN106403641A CN 106403641 A CN106403641 A CN 106403641A CN 201610365863 A CN201610365863 A CN 201610365863A CN 106403641 A CN106403641 A CN 106403641A
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- fin
- sample
- angle
- 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.)
- Pending
Links
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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
-
- 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
Abstract
The invention provides a heat exchanger and a refrigeration cycle apparatus. This heat exchanger is equipped with: a pair of header pipes which are arranged in parallel vertically in the direction of gravity; a plurality of heat transfer pipes which are juxtaposed parallel to the direction of gravity and are bonded between the pair of header pipes; and a plurality of fins which are bonded between adjacent heat transfer pipes. The heat transfer pipes and the fins are subjected to hydrophilic surface treatment. Each of the fins has an inclined portion which extends at an angle between the portions where the fin is bonded to the heat transfer pipes. The fin is subjected to water-sliding surface treatment so that the falling angle is smaller than the inclination angle and is lower than 20 degrees, and the angle between the tangent line of a joint of the droplets on the inclined portion of each fin and joint of each fin, and the inclined portion of each fin is a contact angle, the contact angle is lower than 40 degrees. In addition, the refrigeration cycle apparatus is equipped with a heat exchanger.
Description
Technical field
The present invention relates to having gelled heat exchanger and the refrigeration employing this heat exchanger
EGR.
Background technology
As the conventional gelled heat exchanger of tool, there is a kind of parallel flow heat exchanger,
It has：There are fin, hydrophilic collector and the hydrophilic flat tube on hydrophobic surface
(for example, referring to patent document 1).Also there is following heat exchanger, it has with water proofing property
The hydrophobic fin that coating carries out overlay film to the metal surface after roughening process (for example, is joined
According to patent document 2).
Patent document 1：Japanese Unexamined Patent Publication 2013-190169 publication
Patent document 2：Japanese Unexamined Patent Publication 6-79820 publication
However, in patent document 1 and patent document 2, playing as evaporimeter in heat exchanger
In the case of function, the water droplet producing heat exchanger generation enters between the plane of adjacent fin
The bridge joint phenomenon of row bridge joint, thus the problem that the flowing resistance that there is heat exchanger increases.
Content of the invention
The present invention be in order to solve that above-mentioned problem is made it is therefore intended that provide it can be avoided that by
The bridge joint phenomenon of water droplet generation, heat exchanger and kind of refrigeration cycle so as to maintain flowing resistance
Device.
The heat exchanger of the present invention possesses：A pair of collector, they in gravity direction up and down side by side
Configuration；Multiple heat-transfer pipes, they are with gravity direction juxtaposition side by side, and are engaged in the pair of collection
Between pipe；And multiple fin, they are engaged between adjacent described heat-transfer pipe, to described
Hydrophilic surface treatment is implemented on the surface of heat-transfer pipe, implements water skiing to the surface of described fin
And hydrophilic surface treatment, described fin has inclined plane part, and this inclined plane part is in described fin
Obliquely extend between the bonding part engaging with described heat-transfer pipe, by described inclined plane part with respect to
The angle of horizontal direction is set to the inclination angle of described inclined plane part, will drop to the inclined-plane of described fin
The water droplet in portion is in the case that when starting to fall, the angle of described inclined plane part is set to rolling angle, described tumbles
Angle is less than described inclination angle and is less than 20 °, in the water of the inclined plane part that will be formed in described fin
Drip the angle formed by inclined plane part of the tangent line of junction contacting with described fin and described fin
In the case that degree is set to contact angle, described contact angle is less than 40 °.
Preferably, the surface treatment of water skiing is implemented to the surface of described heat-transfer pipe.
Preferably, the hydrophily on the surface than described fin for the hydrophily on the surface of described heat-transfer pipe
High.
In addition, the refrigerating circulatory device of the present invention possesses above-mentioned heat exchanger.
According to the present invention, due to hydrophilic surface treatment is implemented to fin, by this condensed water or
The water that person's frost after defrosting operating melts generation soaks on a heat sink and extends such that it is able to avoid
The bridge joint phenomenon being produced by water droplet.In addition, by so that the rolling angle of fin is more oblique than fin
The mode that the inclination angle of face is little implements hydrophilic surface treatment it is thus possible to improve to fin
The drainage of water after condensed water and defrosting.Therefore avoid by water droplet in accordance with the invention it is possible to provide
The bridge joint phenomenon producing, the heat exchanger being able to maintain that flowing resistance and refrigerating circulatory device.
Brief description
Fig. 1 is the master of the structure of heat exchanger 10 briefly illustrating embodiments of the present invention 1
View.
Fig. 2 be from upper header 1a side observe embodiments of the present invention 1 heat exchanger 10 flat
The simple partial enlarged drawing of one example of the construction of flat pipe 2 and corrugated fin 3.
Fig. 3 be from upper header 1a side observe embodiments of the present invention 1 heat exchanger 10 flat
The simple partial enlarged drawing of the variation of construction of flat pipe 2 and corrugated fin 3.
Fig. 4 be from upper header 1a side observe embodiments of the present invention 1 heat exchanger 10 flat
The simple partial enlarged drawing of other variation of construction of flat pipe 2 and corrugated fin 3.
Fig. 5 is of the refrigerating circulatory device 100 briefly illustrating embodiments of the present invention 1
The refrigerant loop figure of example.
Fig. 6 is to amplify to represent by a part for the heat exchanger 10 of embodiments of the present invention 1
The size of corrugated fin 3 and the schematic drawing of angle.
Fig. 7 is the schematic drawing of the measuring method of contact angle θ illustrating embodiments of the present invention 1.
Fig. 8 is the schematic drawing of the measuring method of rolling angle Φ illustrating embodiments of the present invention 1.
Fig. 9 is to illustrate in embodiments of the present invention 1 with arbitrary hydrophilic material and arbitrary
The combination of surface roughness be surface-treated after the measurement contact angle θ of sample 4 of aluminum and rolling
The figure of angle of fall Φ.
Figure 10 is the master of the structure of heat exchanger 10 briefly illustrating embodiments of the present invention 2
View.
Figure 11 is the master of the structure of heat exchanger 10 briefly illustrating embodiments of the present invention 3
View.
Description of reference numerals：1a ... upper header；1b ... lower collector pipe；2nd, 6,7 ... flat tube；2a…
Refrigerant flow path；3 ... corrugated fins；3a ... top；3b ... inclined plane part；3c ... incised notch portion；
4 ... measurement samples；5 ... water droplets；5a ... contact；The front inlet side of 5b ...；5c ... initial position；10…
Heat exchanger；20 ... compressors；30 ... cold-producing medium stream circuit switching devices；40 ... heat source side heat exchanges
Device；50 ... decompressors；60 ... load-side heat exchangers；70 ... Air Blast fans；100 ... refrigeration
EGR.
Specific embodiment
Embodiment 1
The construction of the heat exchanger 10 of embodiments of the present invention 1 is illustrated.Fig. 1 is letter
The front view of the construction of heat exchanger 10 of present embodiment 1 slightly is shown.
In addition, closing in the size that in the following accompanying drawing including Fig. 1, there is each component parts
System and shape and actual different situation.In addition in figures in the following, to same or like
Part or part mark identical reference or omit mark reference.And with
Each component parts position relationship (for example, upper and lower relation etc.) each other in lower explanation is essentially
The heat exchanger 10 of the following embodiment including present embodiment 1 is configured to
The position relationship during state using.
The heat exchanger 10 of present embodiment 1 is corrugated fin type heat exchanger, is to make heat
The longitudinal-flow heat exchanger that exchange media (such as cold-producing medium) circulates along the vertical direction.In this enforcement
In the heat exchanger 10 of mode 1, upper header 1a and lower collector pipe 1b are to become a pair of collector
Mode, configuring side by side up and down in gravity direction.
Between upper header 1a and lower collector pipe 1b, with gravity direction be bonded to side by side multiple flat
Pipe 2 (example of heat-transfer pipe), this flat tube 2 is for via upper header 1a or lower collector pipe 1b
The cold-producing medium flowing of distribution.For example in the heat exchanger 10 of present embodiment 1, multiple flat
The flat horizontal surface of pipe 2 is configured to face each other.
It is configured with fin between the flat horizontal surface of two adjacent flat tubes 2, such as corrugated dissipates
Backing 3.That is, heat exchanger 10 becomes the length direction along upper header 1a (or lower collector pipe 1b)
Alternately it is configured with flat tube 2 and the structure of corrugated fin 3.Corrugated fin 3 is ripple
The metal plate of line shape (wavy), have alternately engage with flat in two adjacent flat tubes 2
Multiple top 3a of plane and alternately prolonging between the top 3a of two adjacent flat tubes 2
The multiple inclined plane part 3b stretching.
In the heat exchanger 10 of present embodiment 1, in wind pushing air and in the inside of flat tube 2
Carry out heat exchange between the cold-producing medium flowing along the vertical direction, wherein, wind pushing air with flat tube
The length direction both sides of 2 length direction and upper header 1a (or lower collector pipe 1b) intersect (example
As orthogonal) side flow up.
For example, it is contemplated that the situation that cold-producing medium flows towards lower collector pipe 1b from upper header 1a.It is flowed into
The cold-producing medium of the upper header 1a of heat exchanger 10 is logical to the radical equal number with flat tube 2
Road shunts.The cold-producing medium being split flows downwards in multiple flat tubes 2.In multiple flat tubes
The cold-producing medium flowing downwards in 2 passes through multiple flat tubes 2 and corrugated fin 3, and send
Wind air carries out heat exchange.Cold-producing medium after carrying out heat exchange in multiple flat tubes 2, in next part
Pipe 1b collaborates and flows out from heat exchanger 10.
Next, the water droplet heat exchanger 10 of present embodiment 1 being generated using Fig. 2～Fig. 4
Drainage path illustrate.Fig. 2 is the heat friendship observing present embodiment 1 from upper header 1a side
The simple office of one example of the construction of the flat tube 2 of parallel operation 10 and corrugated fin 3
Portion's enlarged drawing.Fig. 3 be from upper header 1a side observe present embodiment 1 heat exchanger 10 flat
The simple partial enlarged drawing of the variation of construction of flat pipe 2 and corrugated fin 3.Fig. 4
It is the flat tube 2 of heat exchanger 10 and the ripple from upper header 1a side observation present embodiment 1
The simple partial enlarged drawing of other variation of the construction of shape fin 3.As Fig. 2～Fig. 4 institute
Show, the flat tube 2 of the heat exchanger 10 of present embodiment 1 is formed as internally being configured with multiple
The structure of refrigerant flow path 2a.
As shown in Fig. 2 heat exchanger 10 can be configured to：Make corrugated fin 3 with flat
The bonding part of flat pipe 2 joint that is, the width in the major diameter direction of the width ratio flat tube 2 of top 3a
Degree is short.In present embodiment 1, by making the major diameter side of the width ratio flat tube 2 of top 3a
To width short, thus, it is possible to not engaging between the adjacent flat tube 2 of corrugated fin 3
Region as drainage path so that the water melting in heat exchanger 10 flows down towards lower collector pipe 1b.
In addition, as shown in figure 3, it is also possible to shape in the heat exchanger 10 of present embodiment 1
Become following structure：The drainage path pair with heat exchanger 10 on the major diameter direction of flat tube 2
The position of the inside of flat tube 2 answered, is not provided with refrigerant flow path 2a.In addition in fig. 2, lead to
Cross the major diameter direction of the width ratio flat tube 2 making inclined plane part 3b width short constituting drainage path,
But can also be configured to as shown in Figure 4：Corrugated fin 3 on the major diameter direction of flat tube 2
Multiple junction surfaces same position setting incised notch portion 3c, and by the use of incised notch portion 3c as heat exchange
The drainage path of device 10.
In the heat exchanger 10 of present embodiment 1, because corrugated fin 3 is configured to ripple
The metal plate of shape, thus, it is possible to increase the face contacting with wind pushing air such that it is able to efficiently
Carry out the heat exchange with wind pushing air.In addition in heat exchanger 10, except flat tube 2 and
Outside the shape of corrugated fin 3, size and spacing, always according to flat tube 2 and ripple
The surface characteristic of shape fin 3, to determine use refrigerant amount, the heat exchange of heat exchanger 10
Characteristic and manufacturing.
Next, saying to the material of the heat exchanger 10 constituting embodiments of the present invention 1
Bright.
The upper header 1a of heat exchanger 10, lower collector pipe 1b, flat tube 2 and corrugated fin
3 can higher by thermal conductivity, cheap and excellent in workability metal part be constituted.For example,
Heat exchanger 10 can be made up of the part of aluminum or aluminium alloy.
In addition, the part that heat exchanger 10 is used is not limited to aluminium or aluminium alloy, as long as
The part of excellent thermal conductivity then can use arbitrary part.For example can also be by copper, silver, gold etc.
Metal part is constituted.
In addition it is also possible to each of heat exchanger 10 is constituted by different types of metal part
Inscape.For example, it is also possible to upper header 1a and lower collector pipe are constituted by the part of aluminium alloy
1b, and it is made up of flat tube 2 and corrugated fin 3 part made of copper.But by difference
In the case that the metal of species constitutes each inscape of heat exchanger 10, need to pay attention to each part
Current potential design (in the above example, for example to go up at the junction surface of different types of metal
Collector 1a and the junction surface of flat tube 2) do not produce the cold-producing medium leakage causing because of corrosion.
The junction surface of upper header 1a and lower collector pipe 1b and flat tube 2 and flat tube 2 and ripple
The junction surface of line shape fin 3, for example, processed by soldering and engage.In addition, as this joint
The joint method in portion, as long as the method being able to maintain that the thermal conductivity at this junction surface, then can make
Method beyond being processed with soldering, for example, this junction surface can also be connect by welding or bonding
Close.
Next, using the kind of refrigeration cycle to the heat exchanger 10 using present embodiment 1 for the Fig. 5
Device 100 illustrates.Fig. 5 is the refrigerating circulatory device 100 briefly illustrating present embodiment 1
An example refrigerant loop figure.
As shown in figure 5, refrigerating circulatory device 100 has following structure, that is,：Join via cold-producing medium
Pipe and by compressor 20, cold-producing medium stream circuit switching device 30, heat source side heat exchanger 40, decompression
Device 50 and load-side heat exchanger 60 connect circlewise.The heat exchanger of present embodiment 1
10 at least one party being used for heat source side heat exchanger 40 or load-side heat exchanger 60.In addition, system
SAPMAC method device 100 has Air Blast fan 70, for sending air heat source side heat exchanger 40
Wind.
In addition, in Figure 5, as the kind of refrigeration cycle carrying out cooling operation and heating operation both sides
Device 100, only illustrates the inscape of necessary irreducible minimum.Refrigerating circulatory device 100 is except tool
It is also possible to possess gas-liquid separator, receiver, accumulator outside standby inscape shown in Fig. 5
Deng.
Compressor 20 is that the low pressure refrigerant sucking is compressed, and as high-pressure refrigerant row
The fluid machinery going out.
Cold-producing medium stream circuit switching device 30 is in cooling operation and during heating operation to kind of refrigeration cycle
The device that the flow direction of inner refrigerant switches over, such as using cross valve etc..
Heat source side heat exchanger 40 is in heating operation as evaporimeter function, in refrigeration
As the heat exchanger of radiator (such as condenser) function during operating.Hand in heat source side heat
The cold-producing medium internally being circulated in parallel operation 40 is (outside with the air blown by Air Blast fan 70
Air) between heat exchange.
Decompressor 50 is reduced pressure to high-pressure refrigerant and is become low pressure refrigerant.As decompression
Device 50, such as using can adjust linear electron expansion valve (LEV) of aperture etc..
Load-side heat exchanger 60 is as radiator (for example, condenser) in heating operation
Function, the heat exchanger as evaporimeter function in cooling operation.In load-side heat
In exchanger 60, the cold-producing medium that for example internally circulated with by load-side Air Blast fan (not
Diagram) heat between the air (for example, in the case of air-conditioning device be room air) blown
Exchange.
Here, " heating operation " is directed to the refrigeration that load-side heat exchanger 60 supplies HTHP
The operating of agent, " cooling operation " is directed to the refrigeration that load-side heat exchanger 60 supplies low-temp low-pressure
The operating of agent.The flowing of cold-producing medium during heating operation is shown with the arrow of solid line in Figure 5, and
The flowing of cold-producing medium during cooling operation is shown with the arrow of dotted line.
For example, in the air-conditioning dress that refrigerating circulatory device 100 is configured to air conditioning for automobiles or building
In the case of putting, load-side heat exchanger 60 is contained in indoor side unit (not shown), heat source side
Heat exchanger 40 is contained in outdoor side unit (not shown).Sky in air conditioning for automobiles or building
Adjust in device, by supplying the system of HTHP to the load-side heat exchanger 60 of indoor side unit
Cryogen, to carry out heating operation.In addition, in the air-conditioning device of air conditioning for automobiles or building,
By supplying the cold-producing medium of low-temp low-pressure to the load-side heat exchanger 60 of indoor side unit, to enter
Row cooling operation.
In refrigerating circulatory device 100, in long-time continuation cooling operation or heating operation,
Sometimes in the heat source side heat exchanger 40 as evaporimeter function or load-side heat exchange
The heat-transfer pipe (such as flat tube 2) of device 60 or fin (such as corrugated fin 3)
Surface, produces the moisture film (condensation) being caused by condensed water (dew) or frosting.Producing
In the case of condensed water, adhere to and accumulate a part for condensed water on a heat sink, with gravity
And from fin surface flowing.However, not arranging with gravity in the condensed water being attached to fin
In the case of going out or when fin creates frosting, due to fin moisture film or frosting and
Heat source side heat exchanger 40 or the air flow circuit of load-side heat exchanger 60 is made to narrow, thus existing
The inaccessible situation of air flow circuit.If producing in heat source side heat exchanger 40 or load-side heat exchanger 60
The raw narrow road (narrowization) of air flow circuit or the obturation of air flow circuit, then resistance to heat and logical
Wind resistance increases, the therefore heat exchange of heat source side heat exchanger 40 or load-side heat exchanger 60
Rate reduces.
Therefore, in refrigerating circulatory device 100, continue cooling operation or heat fortune long-time
When turning, carry out defrosting operating.Here, " defrosting operating " refers to operate as follows：In order to prevent frost
It is attached to the heat source side heat exchanger 40 as evaporimeter function or load-side heat exchanger
60, or in order that the frost thawing of attachment, and from compressor 20 heat source side heat exchanger 40 or
Person's load-side heat exchanger 60 supplies the hot gas of the gas refrigerant as HTHP.Attachment
In frost and the ice of heat source side heat exchanger 40 or load-side heat exchanger 60, in defrosting operating
When because supply melt to the hot gas of heat source side heat exchanger 40 or load-side heat exchanger 60
Solution.
In the case that the stipulated time continues cooling operation or heating operation, for example, utilize cold-producing medium
Flow passage selector device 30 switches the flow direction of cold-producing medium, supplies the system of HTHP to evaporimeter
Cryogen (hot gas) is carrying out defrosting operating.In addition, defrosting operating can also continue in the stipulated time
In the case of continuous cooling operation or heating operation, will be pressed with bypass refrigerant pipe arrangement (not shown)
Connect between the outlet of contracting machine 20 and heat source side heat exchanger 40 or load-side heat exchanger 60
Connect, and direct from compressor 20 heat source side heat exchanger 40 or load-side heat exchanger 60
Supply hot gas to carry out.
On the other hand, in defrosting operating, due to needing to interrupt common operating, therefore produce system
The reduction of the heat exchange performance (COP) of SAPMAC method device 100.
Therefore, heat source side heat exchanger 40 or load-side heat exchanger 60 are formed as suppressing
Condensation and frosting, and can promptly discharge the structure of the water melting in defrosting operating be important
's.Surface of fin and heat-transfer pipe etc., by improving from heat source side heat exchanger 40 or
The drainage of load-side heat exchanger 60, thus, it is possible to the rate of heat exchange fall suppressing condensed water to cause
Low, and the ability of resistance to frosting can be improved.
Next, to present embodiment 1 for improving the flat tube of drainage during defrosting operating
2 and the surface treatment of corrugated fin 3 illustrate.The heat exchanger of present embodiment 1
10, by hydrophilic surface treatment is implemented to flat tube 2 and corrugated fin 3, to carry
Drainage during high defrosting operating.
Surface treatment (surface modification treatment) as flat tube 2 and corrugated fin 3,
For example there are following methods：Coat flat tube 2 and corrugated fin 3 with hydrophilic material
Surface, and the inoranic membrane to hydrophily and water skiing or organic film carry out overlay film.As to flat
The hydrophilic material of the surface coating of flat pipe 2 and corrugated fin 3, can be using arbitrarily
Hydrophilic inorganic material or organic material, though not limiting, for example can be using comprising water
Glass, silicic acid, polyvinyl alcohol, polyacrylamide, polyacrylic acid, epoxy resin, scaling powder etc.
Material more than one of material composition.
In addition, implement the flat of the aluminum coated steel of hydrophily and water skiing as raising further
The surface treatment of the water skiing on the surface of pipe 2 and corrugated fin 3, for example make overlay film in
The surface roughness of the inoranic membrane on flat tube 2 and corrugated fin 3 surface or organic film is put down
The method of smoothization.In addition, improving the water skiing on the surface of flat tube 2 and corrugated fin 3
Method, be not limited to make the method that surface roughness planarizes, for example also can be flat by adjusting
The surface configuration of flat pipe 2 and corrugated fin 3 is improving water skiing.
Next, illustrating to inclination angle phi f of the corrugated fin 3 of heat exchanger 10.
Fig. 6 is by the part amplification of the heat exchanger 10 of present embodiment 1, to represent ripple
The size of shape fin 3 and the schematic drawing of angle.Here, by between adjacent flat tube 2
Distance (the fin width of corrugated fin 3) is set to w (mm).And corrugated is dissipated
Inter fin space (fin interval) between the adjacent centre position of inclined plane part 3b of backing 3
It is set to d [mm].And, it is vertical in the flow direction of the cold-producing medium making flat tube 2
In the case of, angle that is, ripple between the vertical line of adjacent flat tube 2 and inclined plane part 3b will be connected
The inclination angle of line shape fin 3 is set to φ f [°].In addition, in present embodiment 1, by inclination angle
The scope of φ f is set to 90 ° of 0 ° of ＜ φ f ＜.In addition in present embodiment 1, fin width w,
Inclination angle phi f of the inter fin space d of corrugated fin 3 and corrugated fin 3 spreads all over
The entirety of heat exchanger 10 is roughly the same.
Inclination angle phi f of corrugated fin 3, using the inter fin space d of corrugated fin 3
Calculated by following formula with the fin width w of corrugated fin 3.
φ f=tan-1(d/w)
In addition, in the conventional heat exchanger 10 employing corrugated fin 3, if radiating
Piece spacing d reduces, then heat exchange area increases, thus improving heat exchange performance.On the other hand,
In the case of producing condensation and frosting in heat exchanger 10, if corrugated fin 3 is scattered
Backing spacing d reduces, then water droplet bridge between the adjacent inclined plane part 3b of corrugated fin 3
Connect and become to be difficult to tumble, thus drainage is deteriorated.Particularly in recent years, sometimes handed over improving heat
For the purpose of the performance of parallel operation 10, the inter fin space d of corrugated fin 3 is designed to extremely narrow,
Thus there is condensate easily bridge joint between the adjacent inclined plane part 3b of corrugated fin 3
Tendency.Result makes the flowing resistance in heat exchanger 10 increase, and rate of heat exchange reduces, thus producing
Even if raw heat exchange area increases, rate of heat exchange also reduces the relation of this compromise.In this embodiment party
In the heat exchanger 10 of formula 1, by carrying out the surface treatment of corrugated fin 3, Neng Gouti
The drainage of the water droplet of high bridge joint on corrugated fin 3 such that it is able to avoid because of condensation and
The reduction of the rate of heat exchange that frosting causes.
Next, to as the hydrophilic index illustrating flat tube 2 and corrugated fin 3
The measuring method of contact angle θ illustrate.
Fig. 7 is the schematic drawing of the measuring method of contact angle θ illustrating present embodiment 1.In this reality
Apply in mode 1, measured using the measurement sample 4 of flat tube 2 and corrugated fin 3 and connect
Feeler θ.In present embodiment 1, using the survey to flat tube 2 and corrugated fin 3
Amount sample 4 drip 10 μ L ion exchange waters and the water droplet 5 that produces measuring contact angle θ.Contact
Angle θ is defined as：Tangent line at the measurement contact 5a that contacts with the surface of water droplet 5 of sample 4 and
Angle between the surface of measurement sample 4 of water droplet 5 contact.In present embodiment 1, contact
Angle θ is the scope of 180 ° of 0 °≤θ [°] ＜, is defined as hydrophily in 90 ° of θ [°] ＜,
It is defined as hydrophobicity during θ [°] >=90 °.If in addition it may be said that contact angle θ diminishes, hydrophily
Uprise, if contact angle θ becomes big, hydrophobicity uprises.
Next, to the index as the water skiing illustrating flat tube 2 and corrugated fin 3
The measuring method of rolling angle Φ illustrate.
Fig. 8 is the schematic drawing of the measuring method of rolling angle Φ illustrating present embodiment 1.In this reality
Apply in mode 1, the measurement with contact angle θ is same, using flat tube 2 and corrugated fin
3 measurement sample 4 is measuring rolling angle Φ.In present embodiment 1, rolling angle Φ is defined
For：Drip 10 μ L ion exchanges to the measurement sample 4 of flat tube 2 and corrugated fin 3
Water, makes measurement sample 4 tilt after dripping 30 seconds, and the front inlet side 5b of water droplet 5 is from water droplet
5 initial position 5c moves the inclination angle measuring sample 4 during about 1mm.In fig. 8,
It is shown in broken lines the position of water droplet 5 before moving, and be shown in solid lines the position of water droplet 5 after movement.
In the measuring method of rolling angle Φ of present embodiment 1, due to making survey in drippage after latter 30 seconds
Amount sample 4 tilts, thus be excluded that front inlet side 5b is because on the hydrophilic surface measuring sample 4
Wetting extends and the impact of movement.Rolling angle Φ be 0 ° of ＜ Φ [°]≤90 ° scope it may be said that
If rolling angle Φ diminishes, water skiing uprises, if rolling angle Φ becomes big, water skiing step-down.
In the corrugated fin 3 of the heat exchanger 10 of present embodiment 1, so that corrugated
The mode that rolling angle Φ of fin 3 is less than inclination angle phi f of corrugated fin 3 implements water skiing
The surface treatment of property.In corrugated fin 3, water skiing is higher, then drainage is got over and improved.
And if, inclination angle phi f of reduction corrugated fin 3, can be by corrugated fin 3
Inter fin space d be designed to less, and increase heat exchange area, thus improving heat exchange performance.
Therefore in present embodiment 1, rolling angle Φ with corrugated fin 3 reduces and improves row
Aqueous, thus improving heat exchange performance.
Fig. 9 is to illustrate in present embodiment 1 with arbitrarily hydrophilic material and arbitrary surface
The combination of roughness be surface-treated after the measurement contact angle θ of sample 4 of aluminum and rolling angle
The figure of Φ.The transverse axis of figure represents contact angle θ, and the longitudinal axis of figure represents rolling angle Φ.Stain on figure
Connecing of the arbitrarily combination of hydrophilic material (membrane material) and arbitrary surface roughness is shown
Feeler θ and rolling angle Φ.
Figure 9 illustrates by measurement sample 4 surface coating hydrophilic material species with
And the combination of the degree of surface roughness of measurement sample 4, can manufacture and there is connecing of various combinations
The measurement sample 4 of the aluminum of feeler θ and rolling angle Φ.Even specifically shown relatively low contact angle
θ (such as less than 40 °) and the scope of relatively low rolling angle Φ (such as less than 20 °), also can
Enough manufacture the measurement sample 4 of aluminum.Surface treatment therefore according to present embodiment 1, can make
Make hydrophily height and the high flat tube of water skiing 2 and corrugated fin 3.
Next, the resistance to frosting ability (suppression to the heat exchanger 10 evaluating present embodiment 1
The performance of frosting) and the experiment of drainage performance illustrate.
As the sample of the heat exchanger 10 of present embodiment 1, prepare 300 × 300 × 15mm
The heat exchanger 10 of size.The inter fin space d of corrugated fin 3 is 1.7mm, ripple
The fin width w of shape fin 3 is 10mm, and inclination angle phi f of corrugated fin 3
For 10 °.And the thickness in flat tube 2 minor axis direction is 2mm.
As the comparison other of the heat exchanger 10 of present embodiment 1, prepare prior art
The sample of four corrugated fin type heat exchangers.Four corrugated fin type heat exchangers
Sample is same with the sample of the heat exchanger 10 of present embodiment 1, is that 300 × 300 × 15mm is big
Little corrugated fin type heat exchanger.In addition, the heat exchanger 10 with present embodiment 1
Sample same, the inter fin space of corrugated fin is 1.7mm, corrugated fin 3
Fin width is 10mm, and the inclination angle of corrugated fin is 10 °.And, with this reality
The sample applying the heat exchanger 10 of mode 1 is same, and the thickness in the minor axis direction of flat tube is 2mm.
The sample of four corrugated fin type heat exchangers, dissipates in each flat tube and corrugated
Backing implements different surface treatments as the sample of past case 1～4.
Table 1 represents the sample of past case 1～4 and the sample of the heat exchanger 10 of present embodiment 1
This contact angle θ and the measurement result of rolling angle Φ.In Table 1, by past case 1～4
Sample is simply recited as " past case 1 ", " past case 2 ", " past case 3 " and " past case 4 ".
In addition the sample of the heat exchanger 10 of present embodiment 1 is simply recited as " embodiment 1 ".
[table 1]
The sample of past case 1 is ripple flat tube and corrugated fin being all not carried out be surface-treated
The sample of line shape fin type heat exchanger.In the sample of past case 1, corrugated fin
Contact angle θ is 86 °, and the contact angle θ of flat tube is 85 °.Even if in addition, making to drop to ripple
The water droplet of shape fin and flat tube tilts to 90 ° of angle, and this water droplet does not tumble yet.
The sample of past case 2 is to implement hydrophobic surface to flat tube and corrugated fin
The sample of the corrugated fin type heat exchanger processing.In the sample of past case 2, corrugated
The contact angle θ of fin is 117 °, and rolling angle Φ is 24 °.The contact angle θ of flat tube is 118 °,
Rolling angle Φ is 24 °.
The sample of past case 3 is flat tube to be implemented with hydrophilic surface treatment and to corrugated
Fin implements the sample of the corrugated fin type heat exchanger of hydrophobic surface treatment.?
In the sample of past case 3, the contact angle θ of corrugated fin is 117 °, and rolling angle Φ is 24 °.
The contact angle θ of flat tube is 51 °.Even if in addition, making the water droplet dropping to flat tube tilt to 90 °
Angle, this water droplet do not tumble yet.
The sample of past case 4 is flat tube to be implemented with hydrophobic surface treatment and so that tumbles
Angle Φ is more than the mode at the inclination angle (10 °) of corrugated fin, and corrugated fin is implemented
The sample of the corrugated fin type heat exchanger of hydrophilic surface treatment.In past case 4
In sample, the contact angle θ of corrugated fin is 14 °, and rolling angle Φ is 30 °.Flat tube
Contact angle θ is 51 °.Even if in addition, making the angle that the water droplet dropping to flat tube tilts to 90 °,
This water droplet does not tumble yet.
On the other hand, the sample of the heat exchanger 10 of present embodiment 1 is that flat tube 2 is implemented
Hydrophilic surface treatment so that rolling angle Φ is less than the inclination angle of corrugated fin 3
The mode of φ f (10 °), implements the sample of hydrophilic surface treatment to corrugated fin 3.
In the sample of the heat exchanger 10 of present embodiment 1, the contact angle θ of corrugated fin 3
For 20 °, rolling angle Φ is 8 °.The contact angle θ of flat tube 2 is 51 °.Even if in addition, making to drip
The water droplet dropping down onto flat tube 2 tilts to 90 ° of angle, and this water droplet does not tumble yet.
Sample with the sample of above past case 1～4 and the heat exchanger 10 of present embodiment 1
This, carried out to the resistance to frosting ability and drainage performance of the heat exchanger 10 of present embodiment 1
Evaluate.
Using heat pamp T1, resistance to frosting ability is evaluated.To by the sample of heat exchanger
The speed of this air measures, and measurement starts up to by the sample of heat exchanger from measurement
The initial surface wind speed (1m/s) of air slows down as the elapsed time till 1/2, as during frosting
Between T1.Heat pamp T1 in the sample of past case 1 is set to 1, by the frosting in each sample
Time T1 is normalized to the ratio with respect to the heat pamp T1 in the sample of past case 1, by
This compares evaluation to the heat pamp T1 measuring.
In addition, for the purpose of mating with the situation that real machine operates, using frosting → defrosting operating as one
The individual cycle, and measure the data of the second period after a cycle that operated, as heat pamp
T1.The data of second circulation after measurement has operated a circulation, due to heat pamp
T1 is affected by the residual water residuing in heat exchanger, thus in the defrosting of first circulation
In the case of having undischarged residual water, the formation speed of frost accelerates.Therefore it is evaluated as heat pamp
T1 is bigger, then resistance to frosting ability is better.
For drainage performance, measure the outlet temperature to heat exchanger after defrosting operating terminates
Elapsed time till 10 ° of degree rising, as defrosting time T2.In addition, from through defrosting time
The weight of the heat exchanger after T2 deducts the weight of heat exchanger during operation start, and measures residual
It is stored in quantity of residual M of heat exchanger.The defrosting time T2 of the sample of past case 1 is set to 1,
And the defrosting time T2 of each sample is normalized to the defrosting time of the sample with respect to past case 1
The ratio of T2, thus compares evaluation to the defrosting time T2 measuring.By past case 1
Quantity of residual M of sample be set to 1, by quantity of residual M of each sample be normalized to respect to
The ratio of quantity of residual M of the sample of past case 1, thus enters to quantity of residual M measured
Go comparative evaluation.Therefore it is evaluated as defrosting time T2 less, then drainage performance is better, residual
Water yield M is less, then drainage performance is better.
Table 2 is to illustrate the sample of past case 1～4 and the heat exchanger 10 of present embodiment 1
The table of the measurement result of the resistance to frosting ability of sample and drainage performance.
[table 2]
In the sample of past case 2, heat pamp T1 becomes 1.10, the sample phase with past case 1
Relatively it is known that only slightly improving resistance to frosting ability.And, defrosting time T2 becomes 0.88,
Quantity of residual M becomes 0.90, it is seen that drainage performance compared with the sample of past case 1
Improve.
In addition, in the sample of past case 3, heat pamp T1 also becomes 1.23, with past case 1
Sample compare it is known that only slightly improving resistance to frosting ability.And, defrosting time T2 becomes
For 0.84, quantity of residual M becomes 0.84, it is seen that row compared with the sample of past case 1
The improvement of aqueous energy.
In the sample of past case 2～3, the surface due to corrugated fin has hydrophobicity,
Therefore improve landing, it is thus regarded that than ever the sample of example 1 drainage performance improve and resistance to
Frosting ability slightly improves.In addition, the sample of past case 3 is different from the sample of past case 2, flat
Flat pipe is hydrophily.In the sample of past case 3, by making flat tube be hydrophily, thus removing
The water capacity after frost easily flows to hydrophilic flat tube from hydrophobic fin.Therefore in past case 3
Sample in, compared with the sample of past case 2, defrosting time T2 and quantity of residual M become
Little.However, in the sample of past case 2～3, after draining, the water after defrosting is in corrugated
Between the inclined plane part of fin bridge, can visually confirm exist in ripple type heat exchanger more
Residual water.It is taken as that compared with past case 1, resistance to frosting ability is only slightly improved.
In addition, in the sample of past case 4, heat pamp T1 becomes 0.96, though with conventional
The sample of example 1 compares, and does not also see the improvement of resistance to frosting ability.In addition, defrosting time T2
Become 0.99, quantity of residual M becomes 0.94, even if compared with the sample of past case 1～3,
It can also be seen that slightly improving drainage performance.
In the sample of past case 4, corrugated fin is configured to：Although being hydrophily, rolling
Angle of fall Φ is bigger than the inclination angle of corrugated fin.Therefore after defrosting operating, because water is to moisten
The surface that the state of wet extension residues in corrugated fin is overall, it is taken as that not seeing resistance to frosting
The improvement of ability.
In addition, in the sample of past case 4, because the water after defrosting is to the table of corrugated fin
Face integrally soaks extension, thus is substantially not visible the inclined plane part in corrugated fin for the water after defrosting
Between bridge joint.However, confirm by visual observation engaging with flat tube in corrugated fin
The water after defrosting and the situation do not discharged is remained from flat tube near junction surface.In past case 4
In sample, flat tube has carried out hydrophobic surface treatment, and corrugated fin has carried out parent
Aqueous surface treatment.Therefore in the sample of past case 4, because the contact angle θ of flat tube is big
In the contact angle θ of corrugated fin, therefore do not carry out the draining to flat tube completely but stagnate
Near junction surface, it is thus regarded that the improvement of drainage performance is slight.
On the other hand, in the sample of the heat exchanger 10 of present embodiment 1, heat pamp T1
Become 1.35, it is seen that the improvement of resistance to frosting ability compared with the sample of past case 1～4.
And, defrosting time T2 becomes 0.78, and quantity of residual M becomes 0.53, with past case 1～4
Sample compare it is seen that the improvement of drainage performance.
In the sample of the heat exchanger 10 of present embodiment 1, it is implemented with hydrophilic surface
The corrugated fin 3 of reason, so that rolling angle Φ of corrugated fin 3 compares corrugated fin
The little mode of inclination angle phi f of 3 inclined plane part 3b implements the surface treatment of water skiing.In this enforcement
In the sample of heat exchanger 10 of mode 1, due to also real in addition to hydrophilic surface treatment
Apply the surface treatment of water skiing, therefore in the water of the moistened surface extension of corrugated fin 3,
Smoothly flow to flat tube 2 and discharge such that it is able to greatly reduce the residual of heat exchanger 10
Water yield M.
Further, since corrugated fin 3 is implemented with the surface treatment of water skiing, therefore in defrosting
After operating, the surface in corrugated fin 3 starts the frost melting, direction before melting completely
Cold-producing medium by flat tube 2 flow and contact with flat tube 2, it is thus regarded that defrosting time T2
Shorten and drainage performance improves.Heat pamp T1 becomes the main cause that big and resistance to frosting ability improves,
It is considered as the quantity of residual M minimizing on the surface of corrugated fin 3.Therefore in this embodiment party
In the sample of heat exchanger 10 of formula 1, implement the corrugated radiating of hydrophilic surface treatment
Piece 3, so that rolling angle Φ of corrugated fin 3 is less than the inclined plane part of corrugated fin 3
The mode of inclination angle phi f of 3b implements the surface treatment of water skiing, thus resistance to frosting ability and row
Aqueous can greatly improve.
As described above, the heat exchanger 10 of present embodiment 1 possesses：In gravity side
To a pair of the collector (upper header 1a, lower collector pipe 1b) configuring side by side up and down and gravity direction
Juxtaposition be engaged in the multiple biographies between a pair of collector (upper header 1a, lower collector pipe 1b) side by side
Heat pipe (for example, flat tube 2) and be engaged in adjacent heat-transfer pipe (for example, flat tube 2)
Between multiple fin (for example, corrugated fin 3), to heat-transfer pipe (for example, flat tube
2) and fin (for example, corrugated fin 3) implement hydrophilic surface treatment, radiating
Piece (for example, corrugated fin 3) have with heat-transfer pipe (for example, flat tube 2) engage
Bonding part (top 3a) between the inclined plane part 3b that obliquely extends, by inclined plane part 3b phase
Angle for horizontal direction is set to inclination angle phi f of inclined plane part 3b, will drop to fin (example
As corrugated fin 3) the water droplet of inclined plane part 3b inclined plane part 3b when starting to fall angle
In the case of being set to rolling angle Φ, by make rolling angle Φ than inclination angle phi f little in the way of to fin
(for example, corrugated fin 3) implement the surface treatment of water skiing.
In addition, the refrigerating circulatory device 100 of present embodiment 1 possesses above-mentioned heat exchanger 10.
In present embodiment 1, implement the corrugated fin 3 of hydrophilic surface treatment,
So that the inclination of the inclined plane part 3b than corrugated fin 3 for rolling angle Φ of corrugated fin 3
The little mode of angle φ f, implements the surface treatment of water skiing.Knot therefore according to present embodiment 1
Structure, the water due to producing in heat exchanger 10 does not become ball, but on corrugated fin 3
Wetting extension, even if therefore it is also possible to prevent water in ripple in the case of inter fin space d is less
Bridge between the adjacent inclined plane part 3b of line shape fin 3.
In addition, by making flat tube 2 be hydrophily, wetting extension on corrugated fin 3
The water capacity easily flows to flat tube 2, and carries out draining from flat tube 2 with gravity and become easy,
Thus drainage improves.Structure therefore according to present embodiment 1, because of the raising of drainage, energy
Enough shorten the defrosting operating time, thus the heat exchanger 10 that can cut down energy consumption can be provided
And refrigerating circulatory device 100.
In addition, by abreast configuring flat tube 2 with respect to gravity direction (vertical),
Thus flow to the water of flat tube 2 from corrugated fin 3, be expelled to down with gravity because of deadweight
Collector 1b is such that it is able to suppression is in overall quantity of residual M remaining of heat exchanger 10.In addition,
In the case that lower collector pipe 1b is the rounded refrigerant piping in section, by making lower collector pipe 1b
Surface is hydrophily or water skiing, thus the water discharged because of deadweight is from the surface of lower collector pipe 1b
Flowing is such that it is able to suppress the delay of the water on surface of lower collector pipe 1b.Therefore according to this embodiment party
The structure of formula 1, the icicle in the case of being prevented from starting again generally to operate after defrosting operating.
As described above, according to the heat exchanger 10 of present embodiment 1 and refrigerating circulatory device 100,
Even if it is also possible to suppression condenses in the case that the inter fin space d of corrugated fin 3 is narrower
Water or the water melting because of defrosting operating are detained such that it is able to suppress to divulge information in heat exchanger 10
The increase of resistance.Therefore according to present embodiment 1, it is possible to increase heat exchanger 10 and refrigeration are followed
The heat exchange performance of loop device 100.Further, since the drainage of heat exchanger 10 can be made to carry
Height, therefore, it is possible to suppress new frosting such that it is able to improve the durability of heat exchanger 10.
Embodiment 2
The construction of the heat exchanger 10 of embodiments of the present invention 2 is illustrated.Figure 10 is letter
The front view of the construction of heat exchanger 10 of present embodiment 2 slightly is shown.Present embodiment 2
Heat exchanger 10 be above-mentioned embodiment 1 heat exchanger 10 a variation.
The flat tube 6 of the heat exchanger 10 of embodiments of the present invention 2, to above-mentioned embodiment 1
Flat tube 2 implement the surface treatment of water skiing.In addition, embodiments of the present invention 2
The construction of heat exchanger 10, constituent material and surface treatment and the heat of above-mentioned embodiment 1
Exchanger 10 is identical, therefore omits the description.
Table 3 is to illustrate the sample of past case 1～4 and the heat exchanger 10 of present embodiment 2
The table of the measurement result of the contact angle θ of sample and rolling angle Φ.Table 4 be illustrate past case 1～
The resistance to frosting ability of the sample of heat exchanger 10 of 4 sample and present embodiment 2 and draining
The table of the measurement result of performance.The measuring method of contact angle θ and rolling angle Φ, past case 1～
4 contact angle θ and the reality of the measurement result of rolling angle Φ, resistance to frosting ability and drainage performance
Measurement result of the resistance to frosting ability of proved recipe method and past case 1～4 and drainage performance etc., with
The heat exchanger 10 of above-mentioned embodiment 1 is identical, therefore omits the description.
[table 3]
[table 4]
In the sample of the heat exchanger 10 of present embodiment 2, flat tube 6 implement hydrophily with
And the surface treatment of water skiing, and so that rolling angle Φ is less than the inclination angle of corrugated fin 3
The mode of φ f (10 °) implements hydrophilic surface treatment to corrugated fin 3.In this reality
Apply in the sample of heat exchanger 10 of mode 2, the contact angle θ of corrugated fin 3 is 20 °,
Rolling angle Φ is 8 °.The contact angle θ of flat tube 6 is 35 °, and rolling angle Φ is 34 °.In addition,
If rolling angle Φ of flat tube 6 reduces, the water skiing of flat tube 6 improves, thus drainage performance
Also improve.
In the sample of the heat exchanger 10 of present embodiment 2, heat pamp T1 becomes 1.39,
It is seen that the improvement of resistance to frosting ability compared with the sample of past case 1～4.When in addition defrosting
Between T2 become 0.77, quantity of residual M becomes 0.50, compared with the sample of past case 1～4,
The improvement of drainage performance can be found out.
The resistance to frosting ability of the sample of heat exchanger 10 of present embodiment 2 and drainage performance,
It is seen that entering one compared with the sample of heat exchanger 10 of the above-mentioned embodiment 1 shown in table 2
The tendency that step is improved.In present embodiment 2, rolling angle Φ on flat tube 6 surface is 34 °,
The water skiing on flat tube 6 surface improves.The water therefore residuing in flat tube 6 surface is expelled to next part
Pipe 1b, quantity of residual M reduces, it is thus regarded that resistance to frosting ability and drainage performance obtain into one
Step is improved.
As described above, the multiple heat-transfer pipes to the heat exchanger 10 of present embodiment 2
(for example, flat tube 6) implement the surface treatment of water skiing.
In present embodiment 2, by using implementing the water skiing making rolling angle Φ be less than 90 °
Surface treatment flat tube 6, thus, it is possible to reduce the quantity of residual of heat exchanger 10 further
M is such that it is able to improve heat exchange performance further.
Embodiment 3
The construction of the heat exchanger 10 of embodiments of the present invention 3 is illustrated.Figure 11 is letter
The front view of the construction of heat exchanger 10 of present embodiment 3 slightly is shown.Present embodiment 3
Heat exchanger 10 be above-mentioned embodiment 1 heat exchanger 10 another variation.
The hydrophily on flat tube 7 surface of the heat exchanger 10 of embodiments of the present invention 3 compares ripple
The hydrophily on line shape fin 3 surface is high.In addition, the heat friendship of embodiments of the present invention 3
The construction of parallel operation 10, constituent material and surface treatment, the heat exchange with above-mentioned embodiment 3
Device 10 is identical, therefore omits the description.
Table 5 is to illustrate the sample of past case 1～4 and the heat exchanger 10 of present embodiment 3
The table of the measurement result of the contact angle θ of sample and rolling angle Φ.Table 6 be illustrate past case 1～
The resistance to frosting ability of the sample of heat exchanger 10 of 4 sample and present embodiment 3 and draining
The table of the measurement result of performance.The measuring method of contact angle θ and rolling angle Φ, past case 1～
4 contact angle θ and the experiment of the measurement result of rolling angle Φ, resistance to frosting ability and drainage performance
Measurement result of the resistance to frosting ability of method and past case 1～4 and drainage performance etc., and upper
The heat exchanger 10 stating embodiment 1 is identical, therefore omits the description.
[table 5]
[table 6]
In the sample of the heat exchanger 10 of present embodiment 3, flat tube 7 implement hydrophily with
And the surface treatment of water skiing, and so that rolling angle Φ is less than the inclination angle of corrugated fin 3
The mode of φ f (10 °), implements hydrophilic surface treatment to corrugated fin 3, makes in addition
The contact angle θ of flat tube 7 is lower than the contact angle θ of corrugated fin 3.In present embodiment 1
The sample of heat exchanger 10 in, the contact angle θ of corrugated fin 3 is 20 °, rolling angle Φ
For 8 °.The contact angle θ of flat tube 6 is 14 °, and rolling angle Φ is 30 °.
In the sample of the heat exchanger 10 of present embodiment 3, heat pamp T1 becomes 1.44,
It is seen that the improvement of resistance to frosting ability compared with the sample of past case 1～4.In addition, defrosting
Time T2 becomes 0.62, and quantity of residual M becomes 0.46, compared with the sample of past case 1～4
Relatively it is seen that the improvement of drainage performance.
The resistance to frosting ability of the sample of heat exchanger 10 of present embodiment 3 and drainage performance,
Compared with the sample of the heat exchanger 10 of above-mentioned embodiment 1,2 shown in table 2, table 4, energy
Find out the tendency improved further.In present embodiment 3, due to making the contact angle of flat tube 7
θ is lower than the contact angle θ of corrugated fin 3, and therefore the hydrophily of flat tube 7 dissipates than corrugated
The hydrophily of backing 3 is high.In general, in the interface of the different material of hydrophily, water has
Characteristic to the higher side's flowing of hydrophily.It is taken as that the water capacity easily successfully radiates from corrugated
Piece 3 flows to flat tube 7 via the top 3a of corrugated fin 3, and is discharged to lower collector pipe
1b.
As described above, multiple heat-transfer pipe (examples of the heat exchanger 10 of present embodiment 3
As flat tube 7) hydrophily on surface, higher than the hydrophily on multiple corrugated fin 3 surfaces.
In present embodiment 3, it is higher than that corrugated dissipates by the hydrophily making flat tube 7 surface
The hydrophily on backing 3 surface, thus, it is possible to reduce quantity of residual M of heat exchanger 10 further,
So as to improve drainage performance and heat exchange performance further.
Other embodiment
The present invention is not limited to above-mentioned embodiment, without departing from the spirit and scope of the invention
Various modifications can be carried out.For example, in the above-described embodiment, as refrigerating circulatory device 100
Include the example of air-conditioning device, but the refrigeration beyond the present invention can also apply to air-conditioning device is followed
Loop device 100.
In addition, the respective embodiments described above can be mutually combined to implement.
Claims (4)
1. a kind of heat exchanger is it is characterised in that possess：
A pair of collector, their configuring side by side up and down in gravity direction；
Multiple heat-transfer pipes, they are with gravity direction juxtaposition side by side, and are engaged in the pair of collector
Between；And
Multiple fin, they are engaged between adjacent described heat-transfer pipe,
Hydrophilic surface treatment is implemented to the surface of described heat-transfer pipe,
Water skiing and hydrophilic surface treatment are implemented to the surface of described fin,
Described fin has inclined plane part, and this inclined plane part is engaged with described heat-transfer pipe in described fin
Bonding part between obliquely extend,
At the inclination angle that described inclined plane part is set to respect to the angle of horizontal direction described inclined plane part,
When the water droplet dropping to the inclined plane part of described fin is started to fall, the angle of described inclined plane part sets
In the case of rolling angle, described rolling angle is less than described inclination angle and is less than 20 °,
The contact contacting with described fin in the water droplet of the inclined plane part that will be formed in described fin
In the case that the tangent line at place is set to contact angle with the inclined plane part angulation of described fin, described
Contact angle is less than 40 °.
2. heat exchanger according to claim 1 it is characterised in that
The surface treatment of water skiing is implemented to the surface of described heat-transfer pipe.
3. heat exchanger according to claim 1 and 2 it is characterised in that
The hydrophily on the surface than described fin for the hydrophily on the surface of described heat-transfer pipe is high.
4. a kind of refrigerating circulatory device it is characterised in that
Possesses the heat exchanger any one of claims 1 to 3.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPPCT/JP2015/071386 | 2015-07-28 | ||
| PCT/JP2015/071386 WO2017017789A1 (en) | 2015-07-28 | 2015-07-28 | Heat exchanger and refrigeration cycle apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106403641A true CN106403641A (en) | 2017-02-15 |
Family
ID=57885406
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610365863.8A Pending CN106403641A (en) | 2015-07-28 | 2016-05-27 | Heat exchanger and refrigeration cycle apparatus |
| CN201620502356.XU Expired - Fee Related CN205784707U (en) | 2015-07-28 | 2016-05-27 | Heat exchanger and refrigerating circulatory device |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620502356.XU Expired - Fee Related CN205784707U (en) | 2015-07-28 | 2016-05-27 | Heat exchanger and refrigerating circulatory device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPWO2017017789A1 (en) |
| CN (2) | CN106403641A (en) |
| WO (1) | WO2017017789A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111692741A (en) * | 2019-08-01 | 2020-09-22 | 浙江三花智能控制股份有限公司 | Heat exchanger, preparation method thereof and heat exchange system |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7024522B2 (en) * | 2018-03-14 | 2022-02-24 | 株式会社デンソー | Heat exchanger |
| AU2018431665B2 (en) * | 2018-07-11 | 2022-06-02 | Mitsubishi Electric Corporation | Heat exchanger, heat exchanger unit, and refrigeration cycle apparatus |
| WO2020084786A1 (en) * | 2018-10-26 | 2020-04-30 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device using same |
| JP7118238B2 (en) * | 2019-03-05 | 2022-08-15 | 三菱電機株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04263790A (en) * | 1991-02-18 | 1992-09-18 | Zexel Corp | Heat exchanger |
| JPH06331290A (en) * | 1993-05-20 | 1994-11-29 | Mitsubishi Electric Corp | Heat exchanger for air conditioner and its manufacture |
| JPH11166798A (en) * | 1997-12-03 | 1999-06-22 | Sanyo Electric Co Ltd | Functional unit coated with water slippery material |
| JP2006043510A (en) * | 2004-07-30 | 2006-02-16 | Daikin Ind Ltd | Production method for molded product with frost-formation-suppressed coating film |
| JP2006105415A (en) * | 2004-09-30 | 2006-04-20 | Daikin Ind Ltd | Heat exchanger |
| CN1989388A (en) * | 2004-07-30 | 2007-06-27 | 大金工业株式会社 | Refrigeration unit |
| JP2009229040A (en) * | 2008-03-25 | 2009-10-08 | Mitsubishi Electric Corp | Heat exchanger and manufacturing method of heat exchanger |
| JP2010060159A (en) * | 2008-09-01 | 2010-03-18 | Daikin Ind Ltd | Refrigerating device |
| JP2013190169A (en) * | 2012-03-14 | 2013-09-26 | Sharp Corp | Heat exchanger |
| CN103857976A (en) * | 2011-10-03 | 2014-06-11 | 三菱电机株式会社 | Refrigeration cycle device |
| CN104024781A (en) * | 2012-03-14 | 2014-09-03 | 株式会社神户制钢所 | Aluminum fin material |
| CN104411788A (en) * | 2013-03-21 | 2015-03-11 | 日本帕卡濑精株式会社 | Hydrophilic surface treatment agent for aluminum-containing metal heat exchangers having excellent drainage |
-
2015
- 2015-07-28 WO PCT/JP2015/071386 patent/WO2017017789A1/en active Application Filing
- 2015-07-28 JP JP2017530522A patent/JPWO2017017789A1/en active Pending
-
2016
- 2016-05-27 CN CN201610365863.8A patent/CN106403641A/en active Pending
- 2016-05-27 CN CN201620502356.XU patent/CN205784707U/en not_active Expired - Fee Related
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04263790A (en) * | 1991-02-18 | 1992-09-18 | Zexel Corp | Heat exchanger |
| JPH06331290A (en) * | 1993-05-20 | 1994-11-29 | Mitsubishi Electric Corp | Heat exchanger for air conditioner and its manufacture |
| JPH11166798A (en) * | 1997-12-03 | 1999-06-22 | Sanyo Electric Co Ltd | Functional unit coated with water slippery material |
| JP2006043510A (en) * | 2004-07-30 | 2006-02-16 | Daikin Ind Ltd | Production method for molded product with frost-formation-suppressed coating film |
| CN1989388A (en) * | 2004-07-30 | 2007-06-27 | 大金工业株式会社 | Refrigeration unit |
| JP2006105415A (en) * | 2004-09-30 | 2006-04-20 | Daikin Ind Ltd | Heat exchanger |
| JP2009229040A (en) * | 2008-03-25 | 2009-10-08 | Mitsubishi Electric Corp | Heat exchanger and manufacturing method of heat exchanger |
| JP2010060159A (en) * | 2008-09-01 | 2010-03-18 | Daikin Ind Ltd | Refrigerating device |
| CN103857976A (en) * | 2011-10-03 | 2014-06-11 | 三菱电机株式会社 | Refrigeration cycle device |
| JP2013190169A (en) * | 2012-03-14 | 2013-09-26 | Sharp Corp | Heat exchanger |
| CN104024781A (en) * | 2012-03-14 | 2014-09-03 | 株式会社神户制钢所 | Aluminum fin material |
| CN104411788A (en) * | 2013-03-21 | 2015-03-11 | 日本帕卡濑精株式会社 | Hydrophilic surface treatment agent for aluminum-containing metal heat exchangers having excellent drainage |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111692741A (en) * | 2019-08-01 | 2020-09-22 | 浙江三花智能控制股份有限公司 | Heat exchanger, preparation method thereof and heat exchange system |
| CN111692741B (en) * | 2019-08-01 | 2021-09-28 | 浙江三花智能控制股份有限公司 | Heat exchanger, preparation method thereof and heat exchange system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN205784707U (en) | 2016-12-07 |
| JPWO2017017789A1 (en) | 2018-02-22 |
| WO2017017789A1 (en) | 2017-02-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106403641A (en) | Heat exchanger and refrigeration cycle apparatus | |
| US10627175B2 (en) | Heat exchanger and refrigeration cycle apparatus | |
| CN102538297B (en) | Outdoor heat exchanger and heat pump having the same | |
| US20130284416A1 (en) | Heat exchanger and air conditioner | |
| JP6058154B2 (en) | Corrosion resistance life diagnosis parts, heat exchanger, refrigeration air conditioner | |
| CN103930747A (en) | Plate fin-and-tube heat exchanger, and refrigeration and air-conditioning system with same | |
| JP5392371B2 (en) | Heat exchanger fins, heat exchanger and air conditioner | |
| JPWO2018116408A1 (en) | Heat exchanger, method for manufacturing the same, and refrigeration cycle apparatus | |
| JP2016020757A (en) | Manufacturing method for refrigeration cycle device and cross fin tube type heat exchanger used for the same | |
| JP6053693B2 (en) | Air conditioner | |
| CN208419712U (en) | Heat exchanger and air conditioner | |
| JP5627635B2 (en) | Air conditioner | |
| JP2006046695A (en) | Refrigerating device | |
| JP4422590B2 (en) | Return bend and fin-and-tube heat exchangers | |
| JPWO2020178977A1 (en) | Heat exchanger, heat exchanger unit, and refrigeration cycle equipment | |
| JP5250954B2 (en) | Air conditioner | |
| CN105765308B (en) | Outdoor unit and the refrigerating circulatory device for using it | |
| WO2016119369A1 (en) | Water chiller-heater unit with tube-and-plate type compound heat exchanging evaporative condenser | |
| CN202485172U (en) | Drainage device for air condition condensate water | |
| CN219956241U (en) | Heat exchanger with composite structure fins | |
| CN111197819B (en) | Air conditioner outdoor unit, air conditioner and control method of air conditioner | |
| JP2004044909A (en) | Aluminum fin material for heat exchanger, fin, and fin tube type heat exchanger | |
| WO2017072866A1 (en) | Air conditioner and outdoor unit for air conditioner | |
| JP2012154499A (en) | Heat exchanger, and air conditioner | |
| JP2013204914A (en) | Heat exchanger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20170215 |
|
| WD01 | Invention patent application deemed withdrawn after publication |