CN101802539A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
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- CN101802539A CN101802539A CN200880107613.8A CN200880107613A CN101802539A CN 101802539 A CN101802539 A CN 101802539A CN 200880107613 A CN200880107613 A CN 200880107613A CN 101802539 A CN101802539 A CN 101802539A
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- corrugated fin
- fin
- downwind
- weather
- downwind side
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
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- Engineering & Computer Science (AREA)
- Geometry (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A parallel flow heat exchanger in which defrost water and condensate can be drained smoothly while enhancing the heat exchange performance by improving the shape of a corrugate fin. The heat exchanger comprises a plurality of horizontal header pipes arranged in parallel at intervals in the vertical direction, a plurality of vertical flat tubes arranged between the header pipes at intervals in the horizontal direction while interconnecting the internal refrigerant passages with the interior of the header pipe, and corrugated fins arranged between the flat tubes. In the corrugated fin, a windward corrugated fin where the fin surface has a downslope toward the lee side, and a leeward corrugated fin where the fin surface has an upslope toward the lee side are arranged with a clearance in between. The size of the clearance is set to unite a water drop adhering to the lee side end of the windward corrugated fin and a water drop adhering to the windward end of the leeward corrugated fin.
Description
Technical field
The present invention relates to a kind of parallel flow heat exchanger.
Background technology
A kind of parallel flow heat exchanger that is widely used in motorcar air conditioner etc., this parallel flow heat exchanger disposes many flat tubes between many house stewards, make the refrigerant passage of flat tube inside and house steward's internal communication, and between flat tube, dispose corrugated fin.This example can be with reference to patent documentation 1 (Japan Patent open communique spy open 2005-24187 number).
The heat exchanger horizontal arrangement of patent documentation 1 record has many house stewards, and arranged perpendicular has many flat tubes, and the corrugated fin between the flat tube is the mountain valley shape of the depth direction central portion of heat exchanger as the bottom.In the lowest point of corrugated fin part, the position that is connected with flat tube is provided with through hole, if the running that defrosts makes attached to the frost on the heat exchanger melts, and then the water of frost thawing generation is discharged from through hole.
In parallel flow heat exchanger, corrugated fin is not a linearity, but forms the lowest point shape, that is to say, forms to have the dip down inclined-plane and the V font of face that is inclined upwardly, thereby reaches the effect that increases area of dissipation, improves heat exchanger effectiveness.But the problem of existence is how to handle dew or the frost that produces when this heat exchanger used as evaporimeter.
Attached between flat tube or the corrugated fin, then hinder the circulation of air as bloom, heat exchanger effectiveness is reduced.Therefore, the running that must defrost is often melted frost, and this defrosting running is exchanged the effect of evaporimeter and condenser.But, melt the water that the back generates in order to discharge frost, even the through hole as patent documentation 1 record is set, but owing to the surface tension of water produces bridge formation (bridging overlap joint) phenomenon (formation moisture film), so water also is difficult under orifice flow.Between corrugated fin, also produce arch formation,,, can not drip the situation of getting off so water takes place often only owing to form film at this place even water flows to the end of corrugated fin.The water that generates of defrosting not only, same condition also takes place in the dew before the frosting.
In order to address the above problem, for example, if enlarge the diameter of through hole, then the contact area of flat tube and corrugated fin reduces, thereby heat exchange performance is reduced.If make the peak valley spacing of corrugated fin become big, then the area of dissipation of corrugated fin reduces, thereby causes heat exchange performance to reduce.
Summary of the invention
In view of the above problems, the object of the present invention is to provide a kind of parallel flow heat exchanger, improve, can improve heat exchange performance, and water or dew that defrosting generates can be discharged swimmingly by shape to corrugated fin.
To achieve these goals, heat exchanger of the present invention comprises: the house steward of many levels, devices spaced apart configured in parallel in vertical direction; Many vertical flat tubes, along continuous straight runs devices spaced apart configuration between described house steward, the refrigerant passage of the described flat tube of each root inside and described house steward's internal communication; And corrugated fin, be configured between the described flat tube; It is characterized in that described corrugated fin comprises: the weather side corrugated fin, its fin surface is the inclined-plane that dips down towards downwind side; And downwind side corrugated fin, its fin surface is the face that is inclined upwardly towards downwind side, wherein, the downwind side end of described weather side corrugated fin and the weather side end of described downwind side corrugated fin separate gap configuration, and the size in described gap is set at: can make attached to the water droplet of the downwind side end of described weather side corrugated fin with attached to the water droplet of the weather side end of described downwind side corrugated fin to combine.
According to this configuration, because the fin surface of weather side corrugated fin and downwind side corrugated fin has the gradient respectively, so whole corrugated fin extends longlyer on air-flow direction, thereby area of dissipation is increased, and improved heat exchange performance.On the other hand, because the weather side corrugated fin does not closely contact with the downwind side corrugated fin, but separate the downwind side end of gap configuration weather side corrugated fin and the weather side end of downwind side corrugated fin, this gap is of a size of and can makes attached to the water droplet of the downwind side end of weather side corrugated fin and the size that combines attached to the water droplet of the weather side end of downwind side corrugated fin, under the situation of the water that so having produced when the defrosting running defrosts generates, if the water droplet of the water droplet of weather side corrugated fin and downwind side corrugated fin converges at gap location, then mutually destroy surface tension each other and combination can not produce bridge formation (bridging overlap joint) phenomenon and flows out from the gap.Therefore, return to when running well, the situation of heat exchange performance can not take place to damage because of the residual droplets freeze that is not discharged from when turning round from defrosting.Because the dew of forming before the frost flows out too, so can not taking place, the area of section of circulation of air path narrows down because of water, thus the situation that heat exchange performance is reduced.
In the heat exchanger of said structure, the downwind side end that also can be by making described weather side corrugated fin and local contact the in weather side end of described downwind side corrugated fin, the described gap of generation on the position beyond the contact site.
According to this configuration, if the downwind side end of weather side corrugated fin and the weather side end of downwind side corrugated fin are docking together, produce local contact, then on the position beyond the contact site, produce the gap, thus can be easily and production efficiency highland assembled heat interchanger.
According to the present invention, in parallel flow heat exchanger, can improve heat exchange performance, and can discharge water or dew that defrosting generates reliably.
Description of drawings
Fig. 1 is the diagrammatic vertical cross-section view of the brief configuration of expression heat exchanger.
Fig. 2 is the cutaway view along the A-A line cut-out of Fig. 1.
Fig. 3 is the amplifier section horizontal cross of heat exchanger.
Fig. 4 is the cutaway view along the B-B line cut-out of Fig. 3.
Fig. 5 is the stereogram of one group of flat tube and corrugated fin.
Fig. 6 is the side view of one group of flat tube and corrugated fin.
Fig. 7 is the one group of flat tube of second embodiment and the stereogram of corrugated fin.
Fig. 8 is the one group of flat tube of second embodiment and the side view of corrugated fin.
Fig. 9 is the one group of flat tube of the 3rd embodiment and the stereogram of corrugated fin.
Figure 10 is the one group of flat tube of the 3rd embodiment and the side view of corrugated fin.
Figure 11 is the one group of flat tube of the 4th embodiment and the stereogram of corrugated fin.
Figure 12 is the one group of flat tube of the 4th embodiment and the side view of corrugated fin.
Figure 13 is the one group of flat tube of the 5th embodiment and the stereogram of corrugated fin.
Figure 14 is the one group of flat tube of the 5th embodiment and the side view of corrugated fin.
Figure 15 is the 6th embodiment and cutaway view Fig. 2 the same manner.
Figure 16 is the 7th embodiment and cutaway view Fig. 2 the same manner.
Figure 17 is the table that the size plumbing in investigation gap brings the experimental result of influence.
Figure 18 is the curve map of the experimental result of Figure 17.
Description of reference numerals
1 heat exchanger
2,3 house stewards
2U, 3U weather side house steward
2D, 3D downwind side house steward
4 flat tubes
4U weather side flat tube
4D downwind side flat tube
5 refrigerant passage
6 corrugated fins
6U weather side corrugated fin
6D downwind side corrugated fin
9 gaps
The specific embodiment
Based on Fig. 1 to Fig. 6 first embodiment of the present invention is described below.Heat exchanger 1 is the house steward 2,3 of two levels of configured in parallel devices spaced apart in vertical direction, between house steward 2,3, devices spaced apart and with many vertical flat tubes 4 of prescribed distance configuration in the horizontal direction makes the internal communication of refrigerant passage 5 and house steward 2,3 in the flat tube 4. Fix house steward 2,3 and flat tube 4 by welding.Between flat tube 4, dispose corrugated fin 6.Fix flat tube 4 and corrugated fin 6 by welding equally. House steward 2,3, flat tube 4 and corrugated fin 6 are made by high-termal conductivity metal (for example aluminium).And in Fig. 1, the paper upside is the upside of vertical direction, and the paper downside is the downside of vertical direction, between the house steward 3 of the house steward 2 of upside and downside, disposes many flat tubes 4 with prescribed distance, makes its long side direction keep vertical.
Owing between house steward 2,3, be provided with many flat tubes 4, and between flat tube 4, be provided with corrugated fin 6,, can carry out heat exchange effectively so the heat radiation of heat exchanger 1 (heat absorption) area is big.End the house steward 3 of downside is provided with cold-producing medium inflow entrance 7, the house steward's 2 of upside a end and be provided with cold-producing medium flow export 8 with the position at 7 one-tenth diagonal angles of cold-producing medium inflow entrance.
Then, based on Fig. 2, Fig. 3, Fig. 5 and Fig. 6 the structure of corrugated fin 6 is described.In Fig. 2, Fig. 3 and Fig. 6, the paper left side is a weather side, and the paper right side is a downwind side, and in Fig. 5, the paper front left side is a weather side, and the paper right lateral side is a downwind side.And, in vertical sectional view as shown in Figure 2, the paper left side is a weather side, and the paper right side is a downwind side, in stereogram as shown in Figure 5, the paper front left side is a weather side, the paper right lateral side is a downwind side, and in side view as shown in Figure 6, the paper left side is a weather side, the paper right side is a downwind side, and above-mentioned windward, the relation of leeward are equally applicable to accompanying drawing that the later embodiment of second embodiment is described.
As Fig. 2, shown in Figure 3, corrugated fin 6 is divided into weather side corrugated fin 6U and downwind side corrugated fin 6D, and they are welded on respectively on the flat tube 4.The fin surface of weather side corrugated fin 6U is the inclined-plane that dips down towards downwind side.The fin surface of downwind side corrugated fin 6D is the face that is inclined upwardly towards downwind side.The sloped of upstroke to descending slope and downwind side corrugated fin 6D of weather side corrugated fin 6U has equal angles.The cross-directional length of weather side corrugated fin 6U on air-flow direction and downwind side corrugated fin 6D equates.
If, then can see a plurality of V fonts that are arranged above and below from observing weather side corrugated fin 6U and downwind side corrugated fin 6D with the mobile rectangular direction of air.But the bottom of V word does not have closed but unlimited.That is to say that weather side corrugated fin 6U does not closely contact with downwind side corrugated fin 6D, but is configured to across gap 9.The size in gap 9 is set at and can combines attached to the water droplet of the downwind side end of weather side corrugated fin 6U with attached to the water droplet of the weather side end of downwind side corrugated fin 6D.
There is not the fan of expression to blow among the figure if utilize, and cold-producing medium is flowed in heat exchanger 1, then under the situation of the operation mode that heat exchanger 1 is used as evaporimeter (for example, in the off-premises station of the separate type air conditioner that constitutes by indoor set and off-premises station, adopt heat exchanger 1, if heating installation running, then heat exchanger 1 works as evaporimeter), heat exchanger 1 absorbs heat from air, and emits cold wind in contrast in air.Because the fin surface of weather side corrugated fin 6U and downwind side corrugated fin 6D has the gradient respectively, so do not have the gradient with corrugated fin but the situation of level is compared, whole corrugated fin 6 extends longlyer on air-flow direction, thereby can obtain good heat exchange performance.
If continue to absorb heat from air, on the surface of the surface of side corrugated fin 6U and downwind side corrugated fin 6D, still being all can dewfall on the surface of flat tube 4 no matter then airborne moisture is in the wind.If initial trickle water droplet is combined into big water droplet, then they flow down along the inclined plane of weather side corrugated fin 6U or downwind side corrugated fin 6D, arrive gap 9.If gap 9 is wide, the downwind side end of the side of then being in the wind corrugated fin 6U or the weather side end of downwind side corrugated fin 6D, water droplet only produces arch formation.But, because being set at, the size in gap 9 can combine attached to the water droplet of the downwind side end of weather side corrugated fin 6U with attached to the water droplet of the weather side end of downwind side corrugated fin 6D, so if 9 places converge the water droplet of the water droplet of weather side corrugated fin 6U and downwind side corrugated fin 6D in the gap, then mutually destroy each other surface tension and combination, thereby can not produce arch formation and 9 flow out from the gap.
In the operation mode (heat exchanger 1 absorbs the operation mode of heat from outdoor air) that heat exchanger 1 is used as evaporimeter, temperature conditions or operating condition according to surrounding air, sometimes airborne moisture can be formed frost, on the surface attached to flat tube 4 or corrugated fin 6.As time passes, the thickness of frost increases, and heat exchange performance is reduced, so the running that must defrost is often melted frost.9 places converge in the gap to melt the water that the back generates as bloom, then destroy mutually each other surface tension and combination, thereby can not produce arch formation and 9 flow out from the gap.Therefore, return to when running well, the situation of heat exchange performance can not take place to damage because of the residual droplets freeze that is not discharged from when turning round from defrosting.
The sloped of upstroke to descending slope and downwind side corrugated fin 6D of weather side corrugated fin 6U can be selected in 5 °～40 ° scope.If gradient steepening, then heat exchange area increases and draining easily, can hinder the circulation of air but then, so can come to determine suitable numerical value by experiment.Other numerical value can exemplify as follows: be spaced apart 5.5mm between the flat tube 4, the thickness of flat tube 4 is 1.3mm, the cross-directional length of weather side corrugated fin 6U on air-flow direction and downwind side corrugated fin 6D is respectively 18mm, the peak valley spacing of weather side corrugated fin 6U and downwind side corrugated fin 6D is respectively 2mm～3mm, and the size in gap 9 is 0.5mm to the maximum.Certainly, these numerical value just illustrate, and are not used in the qualification summary of the invention.
Then, other embodiments of the present invention are described.
Fig. 7, Fig. 8 represent second embodiment of the present invention.The difference of second embodiment and first embodiment is the angle on the inclined plane of weather side corrugated fin 6U and downwind side corrugated fin 6D.That is to say, the downward ratio of slope first embodiment of the weather side corrugated fin 6U of second embodiment slow to descending slope, on the contrary, the sloped of upstroke of downwind side corrugated fin 6D is steeper than the sloped of upstroke of first embodiment.
Fig. 9, Figure 10 represent the 3rd embodiment of the present invention.The 3rd embodiment with the difference of first embodiment is: the position configuration in the gap 9 between weather side corrugated fin 6U and the downwind side corrugated fin 6D becomes from the width center deflection weather side of flat tube 4 on air-flow direction.That is to say, the side of being in the wind corrugated fin 6U and downwind side corrugated fin 6D are under the situation that the cross-directional length on the air-flow direction equates and ratio first embodiment is long, the weather side end of weather side corrugated fin 6U is configured to stretch out from the weather side end of flat tube 4, on the other hand, to be configured to the downwind side end with flat tube 4 be same plane in the downwind side end of downwind side corrugated fin 6D.
In other words, be configured to make weather side corrugated fin 6U and downwind side corrugated fin 6D cross-directional length separately and the gap 9 horizontal direction width sums (the following corrugated fin cross-directional length that is also referred to as sometimes) on air-flow direction, wideer than the width of flat tube 4 on air-flow direction, making the downwind side end of downwind side corrugated fin 6D and the downwind side end of flat tube 4 is same plane.For example, if make weather side corrugated fin 6U and the cross-directional length of downwind side corrugated fin 6D on air-flow direction be respectively 18mm, the horizontal direction width that makes gap 9 is 0.5mm, and then the corrugated fin cross-directional length is 36.5mm.If the width of flat tube 4 on air-flow direction is 30mm, then gap 9 is configured to be positioned at the position from about the center deflection weather side 3mm to 3.5mm of flat tube 4, and 6.5mm is only stretched out from the weather side end of flat tube 4 in the weather side end of weather side corrugated fin 6U.
And, there is no need to make weather side corrugated fin 6U and the cross-directional length of downwind side corrugated fin 6D on air-flow direction to equate.It also can be length difference each other.
Figure 11, Figure 12 represent the 4th embodiment of the present invention.The difference of the 4th embodiment and first embodiment is the length of weather side corrugated fin 6U and downwind side corrugated fin 6D.That is to say, the weather side corrugated fin 6U of the 4th embodiment and the cross-directional length of downwind side corrugated fin 6D on air-flow direction are longer than first embodiment, stretch out from the weather side end of flat tube 4 the weather side end of weather side corrugated fin 6U, and stretch out from the downwind side end of flat tube 4 the downwind side end of downwind side corrugated fin 6D.
Figure 13, Figure 14 represent the 5th embodiment of the present invention.The difference of the 5th embodiment and first embodiment is the length ratio of weather side corrugated fin 6U and downwind side corrugated fin 6D.That is to say, in the first embodiment, the cross-directional length of weather side corrugated fin 6U on air-flow direction and downwind side corrugated fin 6D is equal to each other, but in the 5th embodiment, downwind side corrugated fin 6D is longer than weather side corrugated fin 6U.
Shown in first embodiment to the, five embodiments, by changing the ratio of corrugated fin cross-directional length and flat tube 4 width, perhaps change the relative position of corrugated fin 6 and flat tube 4, can obtain the heat exchanger 1 of multiple mode.
Figure 15 represents the 6th embodiment of the present invention.The difference of the 6th embodiment and first embodiment is the structure of flat tube 4.That is to say, in the first embodiment, on an independent flat tube 4, be welded with weather side corrugated fin 6U and downwind side corrugated fin 6D, but in the 6th embodiment, flat tube is divided into weather side flat tube 4U and downwind side flat tube 4D, be welded with weather side corrugated fin 6U on the side of the being in the wind flat tube 4U, on downwind side flat tube 4D, be welded with downwind side corrugated fin 6D.
Figure 16 represents the 7th embodiment of the present invention.The 7th embodiment is the further improvement to the 6th embodiment.That is to say, in the 7th embodiment, flat tube not only, house steward also is divided into weather side house steward 2U, 3U and downwind side house steward 2D, 3D.
The respective embodiments described above then can be implemented as long as structurally there is not contradiction in a plurality of combinations.
Because gap 9 is the distances between the weather side end of the downwind side end of weather side corrugated fin 6U and downwind side corrugated fin 6D, so the distance of horizontal direction not only, the distance of vertical direction also is the key element in gap 9.For example, in the structure of Fig. 2, because the downwind side end of weather side corrugated fin 6U is consistent with the height of the weather side end of downwind side corrugated fin 6D, so only determine the size in gap 9 by the horizontal direction distance at both ends.At this,, then come together to determine the size in gap 9 by the horizontal direction distance at both ends and vertical direction distance if consider that the downwind side end of weather side corrugated fin 6U is different with the height of the weather side end of downwind side corrugated fin 6D.
For example, can be in the following way.That is to say, as shown in Figure 5 weather side corrugated fin 6U and downwind side corrugated fin 6D are such, on elongated aluminium (for example, the laminal elongated aluminium of rectangle), the mode that tilts to intersect with the long side direction with this material forms undulatory ridge shape.Because the end of such corrugated fin is not very straight, so, then produce the part (contact site) and the part that does not contact (noncontact portion) of contact if two ends are docking together.Can be noncontact portion as gap 9.Can excessively not hinder current to come out to determine the ratio of contact site and noncontact portion with existing of contact site.
According to the method described above, when making heat exchanger 1, only need weather side corrugated fin 6U and downwind side corrugated fin 6D are docking together, and be welded on the flat tube 4 and get final product, owing to do not need critically to measure the interval, so improved production efficiency.
The experimental result of the influence that the size plumbing in the table of Figure 17 and the graphical representation of Figure 18 investigation gap 9 brings.In experiment, heat exchanger 1 under water is pulled and measures its quality from water, and the difference of this measured value and heat exchanger 1 dry weight as moisture-holding capacity.Carried out one-shot measurement in per two seconds from moment (elapsed time the is 0) beginning that pulls.The unit of moisture-holding capacity is that the surface area at heat exchanger is 1m in the table
2Situation under (the real surface area of the heat exchanger that converts by this way), keep the quality of water in the above.
The dimensions of the heat exchanger that adopts in above-mentioned experiment is as follows.Promptly, the thickness of flat tube is 1.3mm, gap size between the flat tube is 3.5mm, the horizontal width of the air-flow direction of flat tube is 23mm, the horizontal width of the air-flow direction of the horizontal width of the air-flow direction of weather side corrugated fin and downwind side corrugated fin is 18mm, the vertical-direction length of weather side corrugated fin and downwind side corrugated fin is 160mm, the peak valley spacing of weather side corrugated fin and downwind side corrugated fin is 1.7mm, the wall thickness of weather side corrugated fin and downwind side corrugated fin is 0.1mm, and the gradient of weather side corrugated fin and downwind side corrugated fin is 32 °.
In the curve map of the table of Figure 17 and Figure 18, the state that weather side corrugated fin and downwind side corrugated fin are docking together is as " gap is of a size of 0mm ", beginning with 1mm from this state is that unit separates weather side corrugated fin and downwind side corrugated fin, measures." gap is of a size of 0mm " only at contact site, and has the gap on other positions.Promptly " gap is of a size of 0mm " and do not mean that the weather side corrugated fin and the downwind side corrugated fin between do not have drainage channel.
According to above-mentioned experiment, the gap is that experiment sample more than the 3mm is compared less than the experiment sample of 3mm and gap as can be seen, and after 20 seconds, moisture-holding capacity reduces reliably.This shows that preferred gap is less than 3mm.If the consideration displacement, then the gap can be for below the 2mm.If the drainage speed of considering, then the gap can be for about 1mm.
More than, though embodiments of the present invention are illustrated, scope of the present invention is not limited thereto, and can carry out various changes to the present invention in the scope that does not break away from purport of the present invention.
The present invention can be widely used in parallel flow heat exchanger.
Claims (2)
1. a heat exchanger comprises: the house steward of many levels, devices spaced apart configured in parallel in vertical direction; Many vertical flat tubes, along continuous straight runs devices spaced apart configuration between described house steward, the refrigerant passage of the described flat tube of each root inside and described house steward's internal communication; And corrugated fin, be configured between the described flat tube; It is characterized in that,
Described corrugated fin comprises:
The weather side corrugated fin, its fin surface is the inclined-plane that dips down towards downwind side; And
The downwind side corrugated fin, its fin surface is the face that is inclined upwardly towards downwind side, wherein,
The downwind side end of described weather side corrugated fin and the weather side end of described downwind side corrugated fin separate gap configuration, and the size in described gap is set at: can make attached to the water droplet of the downwind side end of described weather side corrugated fin with attached to the water droplet of the weather side end of described downwind side corrugated fin to combine.
2. heat exchanger according to claim 1 is characterized in that, the downwind side end of described weather side corrugated fin contacts with the weather side end of described downwind side corrugated fin is local, produces described gap on the position beyond the contact site.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007261103A JP4334588B2 (en) | 2007-10-04 | 2007-10-04 | Heat exchanger |
| JP2007-261103 | 2007-10-04 | ||
| PCT/JP2008/064972 WO2009044593A1 (en) | 2007-10-04 | 2008-08-22 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101802539A true CN101802539A (en) | 2010-08-11 |
| CN101802539B CN101802539B (en) | 2012-06-27 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200880107613.8A Expired - Fee Related CN101802539B (en) | 2007-10-04 | 2008-08-22 | Heat exchanger |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2196758B1 (en) |
| JP (1) | JP4334588B2 (en) |
| CN (1) | CN101802539B (en) |
| WO (1) | WO2009044593A1 (en) |
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| CN101975492A (en) * | 2010-10-19 | 2011-02-16 | 广东美的制冷设备有限公司 | Novel heat exchanging device |
| CN103261828A (en) * | 2010-12-22 | 2013-08-21 | 夏普株式会社 | Heat exchanger and air conditioner equipped with same |
| WO2020134097A1 (en) * | 2018-12-28 | 2020-07-02 | 丹佛斯有限公司 | Heat exchanger |
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| CN102012134B (en) * | 2010-10-19 | 2013-07-31 | 广东美的制冷设备有限公司 | Heat exchanger favorable for drainage |
| JP5799382B2 (en) * | 2012-06-07 | 2015-10-28 | 日立アプライアンス株式会社 | Air heat exchanger |
| JP6471345B2 (en) * | 2014-05-29 | 2019-02-20 | パナソニックＩｐマネジメント株式会社 | Heat exchanger |
| CN106175167A (en) * | 2016-08-25 | 2016-12-07 | 苏州德品医疗科技股份有限公司 | A kind of intelligent medicine-chest based on refrigerating system |
| JPWO2019244397A1 (en) * | 2018-06-19 | 2021-06-24 | シャープ株式会社 | Heat exchanger and air conditioner |
| JP2020034184A (en) * | 2018-08-27 | 2020-03-05 | 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． | Heat exchanger and air conditioner |
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| JP2000062446A (en) * | 1998-08-20 | 2000-02-29 | Zexel Corp | Air conditioner for vehicle |
| JP2002257433A (en) * | 2001-02-28 | 2002-09-11 | Toyo Radiator Co Ltd | Multiple plate vaporizer |
| JP2004317002A (en) * | 2003-04-15 | 2004-11-11 | Matsushita Electric Ind Co Ltd | Heat exchanger |
| JP2005024187A (en) | 2003-07-03 | 2005-01-27 | Matsushita Electric Ind Co Ltd | Outdoor heat exchanger for heat pump |
| CN100483046C (en) * | 2003-07-08 | 2009-04-29 | 昭和电工株式会社 | Evaporator |
| JP4275182B2 (en) * | 2007-11-02 | 2009-06-10 | シャープ株式会社 | Heat exchanger |
| JP4930413B2 (en) * | 2008-02-29 | 2012-05-16 | 日本軽金属株式会社 | Heat exchanger |
-
2007
- 2007-10-04 JP JP2007261103A patent/JP4334588B2/en not_active Expired - Fee Related
-
2008
- 2008-08-22 WO PCT/JP2008/064972 patent/WO2009044593A1/en active Application Filing
- 2008-08-22 CN CN200880107613.8A patent/CN101802539B/en not_active Expired - Fee Related
- 2008-08-22 EP EP08792643.2A patent/EP2196758B1/en not_active Not-in-force
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101975492A (en) * | 2010-10-19 | 2011-02-16 | 广东美的制冷设备有限公司 | Novel heat exchanging device |
| CN103261828A (en) * | 2010-12-22 | 2013-08-21 | 夏普株式会社 | Heat exchanger and air conditioner equipped with same |
| CN103261828B (en) * | 2010-12-22 | 2015-11-25 | 夏普株式会社 | Heat exchanger and the air conditioner being provided with this heat exchanger |
| WO2020134097A1 (en) * | 2018-12-28 | 2020-07-02 | 丹佛斯有限公司 | Heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2009092262A (en) | 2009-04-30 |
| EP2196758A4 (en) | 2014-01-15 |
| WO2009044593A1 (en) | 2009-04-09 |
| JP4334588B2 (en) | 2009-09-30 |
| EP2196758B1 (en) | 2017-11-22 |
| EP2196758A1 (en) | 2010-06-16 |
| CN101802539B (en) | 2012-06-27 |
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| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
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Granted publication date: 20120627 |