CN1590924A - Condenser - Google Patents
Condenser Download PDFInfo
- Publication number
- CN1590924A CN1590924A CNA2004100749007A CN200410074900A CN1590924A CN 1590924 A CN1590924 A CN 1590924A CN A2004100749007 A CNA2004100749007 A CN A2004100749007A CN 200410074900 A CN200410074900 A CN 200410074900A CN 1590924 A CN1590924 A CN 1590924A
- Authority
- CN
- China
- Prior art keywords
- condenser
- refrigerant
- phase region
- supercooled liquid
- supercooling tube
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Separation By Low-Temperature Treatments (AREA)
- Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A condenser where a refrigerant introduced from a compressor is coexisting in super-heated vapor, two-phase and super-cooled liquid states combines a plurality of refrigerant pa ths within at least one of super-heated vapor and two-phase regions to output the refrigerant to the super-cooled liquid region, and provides a proper percentage of the super-cooled liq uid region.
Description
Technical field
The present invention relates to a kind of condenser, and more specifically, relate to and a kind ofly come to supercooled liquid tagma output refrigerant and the condenser in the supercooled liquid tagma of suitable percentage is provided by a plurality of refrigerant pipes on one of the superheated steam zone at least in the condenser and two-phase region are merged, wherein the refrigerant of drawing from compressor in condenser exists simultaneously with superheated steam state, two phases and subcooled liquid state.
Background technology
In general, compression refrigeration circulation is finished by a compressor 5, condenser 1, an expansion valve 3 and an evaporimeter 4.At present, the power consumption in the air-conditioning that is made of this compression refrigeration circulation should be reduced to this requirement of minimum level, receive stronger concern.
Therefore, advanced various projects, comprised and improve the chief component performance separately that constitutes the compression refrigeration circulation.
Fig. 1 represents the main frame of a conventional compression refrigerant cycles.
With reference to this accompanying drawing, air-conditioning etc. are brought into play its performance by the cold air that is produced by the compression refrigeration circulation.
More particularly, compression refrigeration circulation be by a gas refrigerant with low-temp low-pressure change into the compressor 5 of the gas refrigerant of HTHP, a gas refrigerant with HTHP change in the expansion valve 3 of condenser 1, liquid refrigerant that liquid refrigerant with middle temperature high pressure changes low-temp low-pressure into of liquid refrigerant of warm high pressure and the evaporimeter 4 that liquid refrigerant with low-temp low-pressure changes the gas refrigerant of high-temperature low-pressure into finish.
Here, described condenser 1 is equipped with a cooling fan, in order to supply outside or outdoor air.
The liquid refrigerant of warm high pressure this condenser 1 that obtains the supply of HTHP gaseous refrigerant from compressor 5 changes it into, and will change the result and flow to expansion valve 3.
At this moment, working fluid (actuating fluid) is experiencing state variation according to the order of steam-like and two phases in described condenser 1.
Under the situation of steam-like or two phases, to compare with liquid state, pressure drop is very high comparatively speaking.For this reason, a lot of take-off lines can be set and reduce pressure drop.
Suppose that fluid has essentially identical mass flow, gas has 1000 times of volumes to liquid, and therefore has about 1000 times flow velocity.In this case, produced pressure drop, more thereby compressor 5 can do work.For fear of this thing happens, pipeline has been carried out bifurcated.
This is explained more fully steam or two-phase fluid have the flow velocity more faster than liquid.Therefore, flow through separately, that is, a plurality of pipelines of bifurcated, a single pipeline is more useful than flowing through constantly.
Because flow velocity has obtained dispersion, so pressure drop has obtained very big reducing.In other words be exactly that the pressure drop ratio flow velocity when flow velocity is high is little when low.
In addition, the pipeline of a plurality of bifurcateds because fluid is flowed through, this pipeline are shorter than single pipeline and the two flow velocity is the same, so pressure drop has obtained reducing.
The meaning that pressure drop obtains reducing means that compressor wants work also to obtain reducing accordingly, thereby the power consumption of compressor has obtained reduction.
Simultaneously, liquid has lower flow velocity and compares with steam or two-phase fluid and only has 1/10th thermal conductivity, thereby there is no need to flow in the mode of disperseing.
In other words, fluid zone increases manyly more, and the two-phase region with good heat-conductivity just reduces fewly more.Therefore, heat exchanger can suffer big more destruction, even heat exchanger also can be destroyed when these two area size are identical.
Therefore, in order to overcome this shortcoming, concentrate by short pipeline liquid and fluid just enough.That is, pipeline is carried out bifurcated or merge.The pipeline that is used for this purpose is a supercooling tube.
About the coefficient of performance (COP), COP represents such value: the value of refrigeration or pyrogenicity ability is divided by employed power consumption.According to domestic (that is, Korea S) commercial power standard, COP to be remained on 3.54 at least, could will be accredited as Grade A such as refrigerator and/or the such air-conditioning equipment of heater this moment.
In order to improve COP, proposed not only to constitute the performance of each chief component of compression refrigeration circulation, but also forced compressor 5 actings scheme still less by replace the mode of increase evaporating pressure to reduce pressure differential with the reduction condensing pressure by raising.But, this method is confined in certain scope.
Fig. 2 represents refrigerant to be incorporated into the processing procedure of exporting then in the condenser by a superheated steam zone, a two-phase region and a supercooled liquid tagma.
As shown in Figure 2, earlier refrigerant has been carried out bifurcated, be introduced into the superheated steam district then, passed each two-phase region again, exported according to their original bifurcated states by each supercooled liquid tagma subsequently.
Like this, as noted above, although because the flow rate of liquid in the supercooled liquid tagma is slow and thermal conductivity is lower, ten/the last one that two-phase region is only arranged, make in the supercooled liquid tagma liquid and needn't flow in the mode of disperseing, but these liquid are exported from each pipeline, thereby have increased liquid (or cold excessively) district, thereby and have reduced the two-phase region with good heat-conductivity.Therefore, the heat exchanger with intended size has caused the result that performance descends and power consumption increases.
Summary of the invention
An object of the present invention is, solve the problems referred to above and/or shortcoming at least, and provide the advantage of at least hereinafter introducing.
Therefore, an object of the present invention is to introduce two-phase region on the path of row heat exchange increasing the gas refrigerant to go in the condenser, and the suitable percentage in the supercooled liquid tagma that can improve the refrigeration output and the coefficient of performance is provided with good heat conveyance performance.
Another object of the present invention is to advance to merge from a plurality of refrigerant paths of the refrigerant of two-phase region output to being used for, to extend to the supercooled liquid tagma.
Another purpose that has again of the present invention is, further provides a supercooled liquid tagma in the condenser that carries out a compression refrigeration circulation, thereby to increase the refrigeration output in the refrigerating system such as air-conditioning.
Aforesaid and other purpose and advantage realizes by following equipment: in a kind of equipment that comprises a compressor and a condenser, wherein the refrigerant of introducing from described compressor exists simultaneously with superheated steam state, two-phase state and subcooled liquid state, provides a plurality of refrigerant paths in one of superheated steam zone and two-phase region at least to merge to extend to a condenser in the supercooled liquid tagma that the rear end part of described two-phase region forms.
According to another aspect of the present invention, the supercooled liquid tagma of wherein said condenser has 7% to 23% the percentage of scope from the refrigerant paths district.
According to the present invention, described refrigerant is by exporting to described supercooled liquid tagma through the refrigerant paths that merges, thereby the described two-phase region with good heat conveyance performance has obtained sufficient increase.In addition, described supercooled liquid tagma is to be provided with suitable percentage, thereby degree of supercooling is improved, and has improved the performance of air-conditioning thus and has reduced its power consumption.
Other advantage, purpose and feature of the present invention will partly provide in the following description, and for a person skilled in the art, other part will become apparent after the content below having studied, and perhaps can figure out by practical application of the present invention.According to the scheme that particularly points out in the appending claims, can realize and obtain objects and advantages of the present invention.
Description of drawings
With reference to the accompanying drawings the present invention is described in detail, wherein identical Reference numeral is represented components identical, wherein:
Fig. 1 represents the chief component of a conventional compression refrigerant cycles;
Fig. 2 represents to be incorporated into refrigerant in the condenser and passes through the processing procedure of superheated steam zone, two-phase region and the output of supercooled liquid tagma subsequently;
Fig. 3 is one and schematically shows the block diagram that comprises according to structure of condenser of the present invention;
Fig. 4 a and 4b represent the state of refrigerant and path and the zone that refrigerant passed through in condenser; With
Fig. 5 a and 5b have represented to show the curve and the form of the relation between the supercooling tube and the coefficient of performance (COP).
The specific embodiment
Following detailed description will be introduced a kind of condenser according to the preferred embodiments of the present invention with reference to accompanying drawing.
Fig. 3 schematically shows a kind of block diagram that comprises according to structure of condenser of the present invention, Fig. 4 a and 4b represent the state of refrigerant in this condenser, path and the zone that this refrigerant passes through, and Fig. 5 is curve map and the form that concerns between the expression supercooling tube and the coefficient of performance.
At first, be introduced with reference to Fig. 3.
Auxiliary valve and dump valve by compressor will be one or more paths from the refrigerant bifurcated of indoor unit (not shown) output, then it be inputed to condenser 1.
Bifurcated of the present invention path is passed the pipeline of superheated steam zone and two-phase region and is merged in the pipeline in supercooled liquid tagma.
And the pipeline that is used for the supercooled liquid tagma occupies the suitable percentage 7%-20% of total pipeline length.At this moment, the performance of the coefficient of performance of air-conditioning (COP) and power consumption has all reached top.
In according to condenser 1 of the present invention, the state of working fluid has experienced according to the variation from steam, two-phase to the order of liquid.
For liquid condition, to compare with steam or two-phase state, pressure drop is relatively low.Therefore, in order to reduce pressure drop, there is no need liquid is carried out bifurcated.
In general, if fluid has identical mass flow, compare with gas so, liquid will have about 1/1000 volume, thereby has about 1/1000 flow velocity.Therefore, if liquid is not carried out bifurcated, so just will be like this really.
Fig. 4 a and 4b represent to be incorporated into refrigerant in the condenser by a plurality of paths (for example, two or three paths) among the present invention and to pass through superheated steam zone, two-phase region and the supercooled liquid tagma processing procedure with its output.
As shown in the drawing, process bifurcated and the refrigerant that is incorporated in the superheated steam zone pass two-phase region separately, thereby flow in the supercooled liquid tagma that merges on the refrigerant paths, and output to expansion valve (the main LEV of Fig. 3) subsequently.
The pipeline that is used for the supercooled liquid tagma occupies suitable percentage, adds up to the 7-20% of pipeline length overall this moment.In this case, air-conditioning has the highest COP and power consumption performance.
Fig. 5 a and 5b are the curve map and the forms of the relation between expression supercooling tube and the COP.
In Fig. 3, the quantity of whole pipelines has been set to two row (row) and 26 rank (step) in the condenser 1.Here, test has provided the relation between whole ducted supercooling tubes and the COP.When supercooling tube is set to two rank (at this moment, supercooling tube account for whole pipelines 7%), recording employed power consumption is 569W, recording refrigeration output simultaneously is 2692W.Like this, trying to achieve COP is 4.73.
When supercooling tube is set to quadravalence (at this moment, supercooling tube account for whole pipelines 15%), recording employed power consumption is 567W, recording refrigeration output simultaneously is 2745W.Like this, trying to achieve COP is 4.84, and the situation that is set to two rank with supercooling tube is compared, and slightly rises.But, when supercooling tube is set to six rank (at this moment, supercooling tube account for whole pipelines 23%), recording employed power consumption is 586W, recording refrigeration output simultaneously is 2726W.Like this, trying to achieve COP is 4.65, and the situation that is set to two joints with supercooling tube is compared, and reduces once more.
From aforementioned content as can be seen, when the shared percentage of the supercooling tube in being installed in condenser reaches 7% to 20% this scope of whole pipelines, can obtain the COP of optimum degree.
In the invention that provides in the above, the refrigerant paths of two-phase region is merged, extending to the supercooled liquid tagma, and show the shared suitable percentage in supercooled liquid tagma, thereby two-phase region has obtained increase.Therefore, efficiency of thermal transfer and COP can be improved, and power consumption can be reduced.
Though the present invention is displaying and the introduction of carrying out with reference to its specific preferred embodiment, but those skilled in the art will be appreciated that, can carry out therein various in form and the change on the details, and can not exceed thought of the present invention and the scope that is limited by the accompanying claims.
For example, the present invention can be applied to carry out the refrigerator of condensation and the other products of execution similar functions.
Therefore, specification of the present invention is only used and is explained the purpose of introduction, and is not the scope that is used to limit claims.
Claims (10)
1. in a kind of equipment that comprises a compressor and a condenser, wherein the refrigerant of introducing from described compressor exists simultaneously with superheated steam state, two-phase state and subcooled liquid state, the described condenser a plurality of refrigerant paths in one of superheated steam and two-phase zone at least merges, to extend to a supercooled liquid tagma.
2. condenser as claimed in claim 1 has wherein carried out merging the rear end that is formed on the pipeline that is used for described two-phase region with the supercooled liquid tagma of extending to being used for from the refrigerant paths of the refrigerant of described two-phase region output.
3. condenser as claimed in claim 2, wherein, because described a plurality of being used for carried out merging to extend to described supercooled liquid tagma from the refrigerant paths of the refrigerant of described two-phase region output, the path that therefore is used for two-phase region has obtained increase.
4. condenser as claimed in claim 3, wherein, because two-phase region has obtained increase, so efficiency of thermal transfer is improved.
5. condenser as claimed in claim 1, wherein bifurcated is one or more and the refrigerant that is incorporated in the described superheated steam zone passes each two-phase region, flow in the supercooled liquid tagma on the path that forms by described one or more merging, and export to and be used to reduce the device of one of temperature and pressure at least.
6. condenser as claimed in claim 5 wherein saidly is used to reduce at least that the device of one of temperature and pressure comprises an expansion valve.
7. condenser according to claim 1, the cold path of wherein said mistake district has 7% to 23% the percentage of scope from the refrigerant paths district of this condenser.
8. as condenser as described in the claim 7, the wherein said pipeline that is used for the supercooled liquid tagma has 7% to 20% the suitable percentage of scope from whole pipelines, thereby the coefficient of performance in the air-conditioning (COP) and power consumption performance become the best.
9. condenser as claimed in claim 1, the quantity of the whole pipelines in the wherein described condenser (1) is set to have two row and 26 rank, and when described supercooling tube is set to two rank, this supercooling tube accounts for 7% of whole pipelines, and when described supercooling tube is set to quadravalence, this supercooling tube accounts for 15% of whole pipelines, and when described supercooling tube was set to six rank, this supercooling tube accounted for 23% of whole pipelines.
10. condenser as claimed in claim 1, wherein described being used for merged from the refrigerant paths of the refrigerant of described two-phase region output, thereby make described refrigerant to be input in the supercooled liquid tagma by one or more refrigerant paths through merging.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020030061149A KR20050023758A (en) | 2003-09-02 | 2003-09-02 | Condenser |
| KR61149/03 | 2003-09-02 | ||
| KR61149/2003 | 2003-09-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1590924A true CN1590924A (en) | 2005-03-09 |
| CN100494814C CN100494814C (en) | 2009-06-03 |
Family
ID=34132223
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100749007A Expired - Fee Related CN100494814C (en) | 2003-09-02 | 2004-08-30 | Condenser |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20050044882A1 (en) |
| EP (1) | EP1512925A3 (en) |
| JP (1) | JP2005077088A (en) |
| KR (1) | KR20050023758A (en) |
| CN (1) | CN100494814C (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102798203A (en) * | 2012-08-29 | 2012-11-28 | 海信（山东）空调有限公司 | Air-conditioning outdoor unit condenser and air-conditioning outdoor unit with condenser |
| CN105972845A (en) * | 2016-03-16 | 2016-09-28 | 合肥天鹅制冷科技有限公司 | Energy-saving economical high-temperature-resistant air conditioner refrigerating system |
| CN106196737A (en) * | 2015-05-29 | 2016-12-07 | 江森自控日立空调技术（香港）有限公司 | Heat exchanger |
| CN105987539B (en) * | 2015-02-03 | 2018-09-18 | 上海海立电器有限公司 | Air conditioner and its heat exchanger |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100490722B1 (en) | 2004-07-23 | 2005-05-19 | 엘지전자 주식회사 | A condenser of refrigerator |
| KR100710352B1 (en) | 2004-11-23 | 2007-04-23 | 엘지전자 주식회사 | Bypassing strainer for refrigerant in air-conditioner ? controlling method for the same |
| US7365973B2 (en) | 2006-01-19 | 2008-04-29 | American Power Conversion Corporation | Cooling system and method |
| US8672732B2 (en) | 2006-01-19 | 2014-03-18 | Schneider Electric It Corporation | Cooling system and method |
| US9568206B2 (en) | 2006-08-15 | 2017-02-14 | Schneider Electric It Corporation | Method and apparatus for cooling |
| US8327656B2 (en) * | 2006-08-15 | 2012-12-11 | American Power Conversion Corporation | Method and apparatus for cooling |
| US8322155B2 (en) | 2006-08-15 | 2012-12-04 | American Power Conversion Corporation | Method and apparatus for cooling |
| US7681404B2 (en) | 2006-12-18 | 2010-03-23 | American Power Conversion Corporation | Modular ice storage for uninterruptible chilled water |
| US8425287B2 (en) | 2007-01-23 | 2013-04-23 | Schneider Electric It Corporation | In-row air containment and cooling system and method |
| US20090138313A1 (en) | 2007-05-15 | 2009-05-28 | American Power Conversion Corporation | Methods and systems for managing facility power and cooling |
| US8219362B2 (en) | 2009-05-08 | 2012-07-10 | American Power Conversion Corporation | System and method for arranging equipment in a data center |
| US8688413B2 (en) | 2010-12-30 | 2014-04-01 | Christopher M. Healey | System and method for sequential placement of cooling resources within data center layouts |
| US9830410B2 (en) | 2011-12-22 | 2017-11-28 | Schneider Electric It Corporation | System and method for prediction of temperature values in an electronics system |
| CN104137105B (en) | 2011-12-22 | 2017-07-11 | 施耐德电气It公司 | Impact analysis on temporal event to the temperature in data center |
| US9791221B1 (en) * | 2012-10-30 | 2017-10-17 | Whirlpool Corporation | Condenser assembly system for an appliance |
| CN102954626B (en) * | 2012-11-08 | 2015-07-08 | 南京师范大学 | Multi-branch indoor heat exchanger for synchronous heat exchange |
| JP6351494B2 (en) * | 2014-12-12 | 2018-07-04 | 日立ジョンソンコントロールズ空調株式会社 | Air conditioner |
| CN106322853B (en) * | 2015-06-30 | 2019-02-05 | 青岛海尔空调器有限总公司 | A kind of single-cooling type condenser pipe system, air conditioner and its application method |
| CN107300266B (en) * | 2017-06-12 | 2019-10-15 | 广东美的制冷设备有限公司 | Air-conditioning system, the control method of air-conditioning system |
| CN111373205B (en) * | 2017-11-29 | 2021-08-10 | 三菱电机株式会社 | Air conditioner |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3843305A1 (en) * | 1988-12-22 | 1990-06-28 | Thermal Waerme Kaelte Klima | CONDENSER FOR A VEHICLE AIR CONDITIONING REFRIGERANT |
| US5224358A (en) * | 1990-10-04 | 1993-07-06 | Nippondenso Co., Ltd. | Refrigerating apparatus and modulator |
| JP3301169B2 (en) * | 1992-11-06 | 2002-07-15 | 株式会社デンソー | Refrigeration equipment |
| DE4245046C8 (en) * | 1992-11-18 | 2008-08-21 | Behr Gmbh & Co. Kg | Condenser for an air conditioning system of a vehicle |
| JPH109714A (en) * | 1996-06-25 | 1998-01-16 | Hitachi Ltd | Freezer |
| FR2754886B1 (en) * | 1996-10-23 | 1998-12-31 | Valeo Thermique Moteur Sa | COIL CONDENSER FOR REFRIGERATION CIRCUIT, ESPECIALLY OF MOTOR VEHICLE |
| JP3116996B2 (en) * | 1996-10-30 | 2000-12-11 | 株式会社デンソー | Recipient integrated refrigerant condenser |
| JP3185687B2 (en) * | 1996-11-13 | 2001-07-11 | ダイキン工業株式会社 | Heat exchanger |
| JPH10205920A (en) * | 1997-01-24 | 1998-08-04 | Calsonic Corp | Condenser |
| KR100264815B1 (en) * | 1997-06-16 | 2000-09-01 | 신영주 | Multi-stage air and liquid separable type condenser |
| US6009719A (en) * | 1998-05-06 | 2000-01-04 | York International Corporation | System for thermal treating of food products |
| DE19918616C2 (en) * | 1998-10-27 | 2001-10-31 | Valeo Klimatechnik Gmbh | Condenser for condensing the internal refrigerant of an automotive air conditioning system |
| JP2002031436A (en) * | 2000-05-09 | 2002-01-31 | Sanden Corp | Sub-cooling type condenser |
-
2003
- 2003-09-02 KR KR1020030061149A patent/KR20050023758A/en not_active Application Discontinuation
-
2004
- 2004-08-23 EP EP04077385A patent/EP1512925A3/en not_active Withdrawn
- 2004-08-25 JP JP2004245552A patent/JP2005077088A/en active Pending
- 2004-08-30 CN CNB2004100749007A patent/CN100494814C/en not_active Expired - Fee Related
- 2004-08-31 US US10/929,386 patent/US20050044882A1/en not_active Abandoned
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102798203A (en) * | 2012-08-29 | 2012-11-28 | 海信（山东）空调有限公司 | Air-conditioning outdoor unit condenser and air-conditioning outdoor unit with condenser |
| CN102798203B (en) * | 2012-08-29 | 2014-08-27 | 海信（山东）空调有限公司 | Air-conditioning outdoor unit condenser and air-conditioning outdoor unit with condenser |
| CN105987539B (en) * | 2015-02-03 | 2018-09-18 | 上海海立电器有限公司 | Air conditioner and its heat exchanger |
| CN106196737A (en) * | 2015-05-29 | 2016-12-07 | 江森自控日立空调技术（香港）有限公司 | Heat exchanger |
| JP2016223672A (en) * | 2015-05-29 | 2016-12-28 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Heat exchanger |
| CN106196737B (en) * | 2015-05-29 | 2020-04-07 | 日立江森自控空调有限公司 | Heat exchanger |
| US10670311B2 (en) | 2015-05-29 | 2020-06-02 | Hitachi-Johnson Controls Air Conditioning, Inc. | Heat exchanger |
| CN105972845A (en) * | 2016-03-16 | 2016-09-28 | 合肥天鹅制冷科技有限公司 | Energy-saving economical high-temperature-resistant air conditioner refrigerating system |
Also Published As
| Publication number | Publication date |
|---|---|
| US20050044882A1 (en) | 2005-03-03 |
| JP2005077088A (en) | 2005-03-24 |
| EP1512925A3 (en) | 2007-12-26 |
| CN100494814C (en) | 2009-06-03 |
| EP1512925A2 (en) | 2005-03-09 |
| KR20050023758A (en) | 2005-03-10 |
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