CN101858698A - Microchannel heat exchanger - Google Patents
Microchannel heat exchanger Download PDFInfo
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- CN101858698A CN101858698A CN200910131244A CN200910131244A CN101858698A CN 101858698 A CN101858698 A CN 101858698A CN 200910131244 A CN200910131244 A CN 200910131244A CN 200910131244 A CN200910131244 A CN 200910131244A CN 101858698 A CN101858698 A CN 101858698A
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- tube
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
- F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
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- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a microchannel heat exchanger, which comprises two collector tubes, a plurality of flat tubes and a plurality of fins, wherein the ends of the two collector tubes on the same side are respectively provided with a refrigerant inlet and a refrigerant outlet; the flat tubes are orderly arranged between the two collector tubes in the longitudinal direction of the collector tubes, and each flat tube is provided with a plurality of flow holes which are respectively communicated with the two collector tubes; each fin is arranged between adjacent flat tubes; and the flow resistance of the flat tubes gradually decreases from the inlet and outlet of the collector tubes, thereby balancing the flow resistance in each flow path. The invention effectively solves the problem of nonuniform refrigerant flow distribution, and preventing unfavorable partial heat emission from affecting the heat exchange efficiency of the complete machine. Preferably, the variation in the flow resistance of the flat tube is the variation of flow area of the flat tube. Preferably, the density of each flat tube is changed, so that different partial regions have different refrigerant flows. The invention has the advantage of reasonable and reliable structural design.
Description
Technical field
The present invention relates to caloic switching technology field, be specifically related to a kind of micro channel heat exchanger.
Background technology
Heat exchanger has experienced by the evolution of fin-tube type to micro-channel parallel flow heat exchanger.With respect to the conventional tube fin heat exchanger, micro-channel heat exchanger has characteristics such as high heat transfer coefficient, high surface-volume ratio, the low heat transfer temperature difference, low flow resistance, its efficiency and reliability are all higher, are mainly used in family expenses, light-duty business air conditioner and the freezing market of freezing.
Existing micro-channel heat exchanger mainly is made of collector tube, micro-channel flat, fin and side plate.See also Fig. 1, this figure is the overall structure schematic diagram of existing micro-channel heat exchanger.Shown in the figure, be arranged with many flat tubes in parallel between two collector tubes, be provided with some fins between adjacent flat tube, wherein, the two ends of many flat tubes are communicated with two collector tubes respectively, and each flat tube is put in the flow cycle of cold-producing medium with the form of parallel connection.Under the duty, cold-producing medium at first enters first collector tube 7 through refrigerant inlet pipe A, and each flat tube of flowing through then flows into second collector tube 8, after refrigerant outlet pipe B flows out micro-channel heat exchanger.
Cold-producing medium constitutes different flow process passages by each flat tube, and be the example definition with the six roots of sensation flat tube of heat exchanger shown in Fig. 1: the cold-producing medium flow process of first flat tube 1 of flowing through is a first pass, and by that analogy, the cold-producing medium flow process of the 6th flat tube 6 that circulates is the 6th flow process.For the micro-channel heat exchanger that knockout is arranged, the cold-producing medium distribution ratio of flowing through when entering first header, 7 inner chambers behind the knockout is more even, flow through respectively then and enter second collector tube 8 behind each flat tube, the distance that the cold-producing medium that flows out through the 6th flat tube 6 extremely exports farthest, in addition, because the structural parameters of the flat tube that adopts in this micro-channel heat exchanger are identical, therefore, compare the flow resistance maximum of the 6th flow process with other flow processs, the flow minimum.For the micro-channel heat exchanger that does not have knockout, cold-producing medium enter flow into the 6th flat tube 6 behind first collector tube, 7 inner chambers distance farthest, thereby bigger through the flow resistance of the 6th flow process of the 6th flat tube 6, refrigerant flow is littler.
Obviously, the different flow process passages that cold-producing medium is passed through compare as can be known, and the first pass distance is the shortest, the flow resistance minimum, and the 6th flow process distance is the longest, the flow resistance maximum; Pass through the flow path resistance of each flat tube is: first flat tube, 1＜the second flat tube 2＜the 3rd flat tube 3＜the 4th flat tube 4＜the 5th flat tube 5＜the 6th flat tube 6.Therefore, be the trend of successively decreasing gradually through the refrigerant flow of each flow process thereupon and change, thereby caused the problem of flow distribution of refrigerant inequality in each flow process, and then cause heat exchanger to exist local heat exchange not good, influence the complete machine heat exchange efficiency.
In view of this, demand developing a kind of micro channel heat exchanger urgently, with the problem of flow distribution of refrigerant inequality in each flow process passage of effective solution.
Summary of the invention
At above-mentioned defective, the technical problem that the present invention solves is, a kind of micro channel heat exchanger is provided, and with the flow resistance of each flow process of balance, solves the uneven problem of flow distribution of refrigerant.
Micro-channel heat exchanger provided by the invention comprises two collector tubes, some flat tubes and several fins, and wherein, the homonymy end of described two collector tubes is respectively arranged with import and outlet; Described some flat tubes are successively set between two collector tubes along the length direction of collector tube, and each flat tube has several through flow holes and is communicated with two collector tubes respectively; Described several fins are arranged between the adjacent flat tube; The flow resistance of described flat tube is the trend that reduces gradually by import and export place to the import and export place away from collector tube near collector tube and changes.
Preferably, the variation of flat tube flow resistance is specially the variation of flat tube circulation area.
Preferably, along the length direction of collector tube, described some flat tubes are divided into some groups, and the through-flow aperture of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube and changes.
Preferably, the through-flow aperture of every described flat tube is the trend variation that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube.
Preferably, along the length direction of collector tube, described some flat tubes are divided into some groups, and the width of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube to be changed.
Preferably, the width of every described flat tube is the trend variation that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube.
Preferably, along the length direction of collector tube, described some flat tubes are divided into some groups, and the thickness of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube to be changed.
Preferably, the thickness of every described flat tube is the trend variation that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube.
Preferably, along the length direction of collector tube, described some flat tubes are divided into some groups, and the distance in every group of flat tube between adjacent two flat tubes is the trend that reduces gradually by import and export place to the import and export place away from collector tube near collector tube and changes.
Preferably, the distance between adjacent two flat tubes is the trend variation that reduces gradually by import and export place to the import and export place away from the collection liquid line near collector tube.
Micro-channel heat exchanger provided by the invention compared with prior art, the flat tube flow resistance changes by being the trend that reduces gradually near the import and export place of collector tube to the import and export place away from collector tube in this scheme.Because the stream by each flat tube is a parallel pipeline, so the overall presure drop of each stream equates, in the little flat tube of flow resistance higher flow velocity arranged.That is to say, by near the import and export place to roughly the same away from the flat tube inner refrigerant flow at import and export place, along the length direction of collector tube, the air-flow temperature difference by heat exchanger reduces.To sum up, the flow resistance that the present invention can each flow process of balance has solved the uneven problem of flow distribution of refrigerant effectively, and then has avoided local poor heat radiation to influence the heat exchange efficiency of complete machine.
Preferred version of the present invention is adjusted the flow resistance of each flat tube by changing the circulation area of each flat tube; In addition, another preferred version of the present invention is by changing the density that is provided with of each flat tube, thereby changes the refrigerant flow of different regional areas, has reasonable in design, advantage reliably.
Description of drawings
Fig. 1 is the overall structure schematic diagram of existing micro-channel heat exchanger;
Fig. 2, Fig. 3 and Fig. 4 show the cross sectional representation of three kinds of different circulation area flat tubes of a kind of embodiment of micro-channel heat exchanger of the present invention respectively;
Fig. 5, Fig. 6 and Fig. 7 show the cross sectional representation of three kinds of different circulation area flat tubes of second embodiment of micro-channel heat exchanger of the present invention respectively;
Fig. 8, Fig. 9 and Figure 10 show the cross sectional representation of three kinds of different circulation area flat tubes of the third embodiment of micro-channel heat exchanger of the present invention respectively;
Figure 11 is the overall structure schematic diagram of the 4th kind of embodiment of micro-channel heat exchanger of the present invention.
The specific embodiment
The present invention is the improvement design of making on the basis of existing micro-channel heat exchanger, comprises two collector tubes, some flat tubes and several fins, and wherein, the homonymy end of described two collector tubes is respectively arranged with import and outlet; Described some flat tubes are successively set between two collector tubes along the length direction of collector tube, and each flat tube has several through flow holes and is communicated with two collector tubes respectively; Described several fins are arranged between the adjacent flat tube; Compared with prior art, technical essential of the present invention is that the flat tube flow resistance is the trend that reduces gradually by import and export place to the import and export place away from collector tube near collector tube and changes; With the flow resistance of each flow process of balance, effectively solve the uneven problem of flow distribution of refrigerant, avoid local poor heat radiation to influence the heat exchange efficiency of complete machine.
Specify present embodiment below in conjunction with Figure of description.
Embodiment 1:
Annexation between the formation of the described micro-channel heat exchanger of present embodiment and each parts is same as the prior art, will not give unnecessary details herein.Overall structure can be referring to Fig. 1.
The mode of the circulation area of this example by changing each flat tube is adjusted the flow resistance of each flat tube.Specifically see also Fig. 2, Fig. 3 and Fig. 4, show the cross sectional representation of three kinds of different flat tubes of circulation area respectively.As shown in the figure, comparatively speaking, flat tube shown in Fig. 2 is the through flow hole of small-bore, and flat tube shown in Fig. 3 is the through flow hole in middle aperture, and flat tube shown in Fig. 4 is the large aperture through flow hole.
Being without loss of generality, is the arrangement that example specifies different through-flow apertures flat tube with the six roots of sensation flat tube shown in Fig. 1 below.
The flow path resistance of first flat tube 1 and second flat tube 2 is less, adopts the flat tube of the small-bore shown in Fig. 2.The flow path resistance of the 3rd flat tube 3 and the 4th flat tube 4 is bigger, adopts the flat tube in the middle aperture shown in Fig. 3.The flow path resistance of the 5th flat tube 5 and the 6th flat tube 6 is bigger, adopts the wide-aperture flat tube shown in Fig. 4.Like this, can remedy, reach the goal of the invention of each flow path resistance of balance owing to the drag overall differences that the flow resistance difference causes in collector tube in each flow process.
Principle according to this, length direction along collector tube, some flat tubes can be divided into some groups, the through-flow aperture of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube and changes, thereby this programme is applied to different heat exchangers.That is to say that the through-flow aperture of flat tube is not limited to aforementioned three kinds of apertures, as long as identical all in the claimed scope of the application with the design philosophy of this programme.
In addition, for the flow resistance of guaranteeing each flow process is identical, accurately distribute the refrigerant flow of each flow process of flowing through.Preferably, the through-flow aperture of every described flat tube is the trend that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube and changes, and guarantees that the refrigerant flow of each flow process is all identical.
Embodiment 2:
This example also is to adjust the flow resistance of each flat tube by the mode of the circulation area that changes each flat tube.Specifically see also Fig. 5, Fig. 6 and Fig. 7, show the cross sectional representation of three kinds of different flat tubes of width respectively.As shown in the figure, comparatively speaking, the width of flat tube shown in Fig. 5 is less, the wider width of flat tube shown in Fig. 6, the width maximum of flat tube shown in Fig. 7.
The layout principle of the flat tube of different in width is identical with embodiment 1 in the present embodiment.The flow path resistance of first flat tube 1 and second flat tube 2 is less, adopts the less flat tube of width shown in Fig. 5.The flow path resistance of the 3rd flat tube 3 and the 4th flat tube 4 is bigger, adopts the flat tube of the wider width shown in Fig. 6.The flow path resistance of the 5th flat tube 5 and the 6th flat tube 6 is bigger, adopts the flat tube of the width maximum shown in Fig. 7; To remedy drag overall differences owing to the flow resistance difference causes in collector tube in each flow process.
Principle according to this, length direction along collector tube, described some flat tubes are divided into some groups, and the width of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube to be changed, thereby this programme is applied to different heat exchangers.Obviously, the width of flat tube is not limited to aforementioned three kinds of width dimensions.
In addition, for the flow resistance of guaranteeing each flow process is identical, accurately distribute the refrigerant flow of each flow process of flowing through.Preferably, the width of every described flat tube is the trend that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube to be changed, and guarantees that the refrigerant flow of each flow process is all identical.
Embodiment 3:
This example also is to adjust the flow resistance of each flat tube by the mode of the circulation area that changes each flat tube.Specifically see also Fig. 8, Fig. 9 and Figure 10, show the cross sectional representation of three kinds of different flat tubes of thickness respectively.As shown in the figure, comparatively speaking, the thickness of flat tube shown in Fig. 8 is less, the thickness broad of flat tube shown in Fig. 9, the thickness maximum of flat tube shown in Figure 10.
The layout principle of the flat tube of different-thickness is identical with embodiment 1,2 in the present embodiment.The flow path resistance of first flat tube 1 and second flat tube 2 is less, adopts the less flat tube of thickness shown in Fig. 8.The flow path resistance of the 3rd flat tube 3 and the 4th flat tube 4 is bigger, adopts the flat tube of the thickness broad shown in Fig. 9.The flow path resistance of the 5th flat tube 5 and the 6th flat tube 6 is bigger, adopts the flat tube of the thickness maximum shown in Figure 10; To remedy drag overall differences owing to the flow resistance difference causes in collector tube in each flow process.
Principle according to this, length direction along collector tube, described some flat tubes are divided into some groups, and the thickness of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube to be changed, thereby this programme is applied to different heat exchangers.Obviously, the thickness of flat tube also is not limited to aforementioned three kinds of gauges.
In addition, for the flow resistance of guaranteeing each flow process is identical, accurately distribute the refrigerant flow of each flow process of flowing through.Preferably, the thickness of every described flat tube is the trend that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube to be changed, and guarantees that the refrigerant flow of each flow process is all identical.
Embodiment 4:
See also Figure 11, present embodiment is adjusted the refrigerant flow of different regional areas, and is adjusted each flat tube flow resistance by changing the density that is provided with of each flat tube.
As shown in the figure, it is bigger near the flat tube in import A and outlet B zone density to be set, i.e. flat tube negligible amounts, and obviously, the fin height in this zone between adjacent flat tube is higher; Flat tube 10 as shown in FIG. and flat tube 20.It is less that the flat tube that is positioned at the collector tube central region is provided with density, and promptly flat tube quantity is more, and the fin height in this zone between adjacent flat tube is lower; Flat tube 30 as shown in FIG. and flat tube 40.Flat tube away from import A and outlet B zone is provided with the density minimum, and the fin height between the adjacent flat tube in this zone is minimum; Flat tube 50 as shown in FIG. and flat tube 60.
Principle according to this, along the length direction of collector tube, described some flat tubes are divided into some groups, and the distance in every group of flat tube between adjacent two flat tubes is the trend that reduces gradually by import and export place to the import and export place away from collector tube near collector tube and changes.Preferably, the distance between adjacent two flat tubes is the trend variation that reduces gradually by import and export place to the import and export place away from the collection liquid line near collector tube.
Should be appreciated that aforementioned four kinds of technical measures that embodiment taked are not limited to independent application, according to actual needs, aforementioned two kinds, three kinds or four kinds of technical measures applied in any combination can be obtained best result of use.In addition, the shape of cross section of the through-flow aperture of flat tube is not limited to the legend shape shown in the accompanying drawing, such as, square opening etc.
In addition, the present invention is equally applicable to fin-tube type heat exchanger by the design philosophy that the flow resistance of adjusting flat tube changes each flat tube inner refrigerant flow, uses needs all in the claimed scope of the application as long as satisfy.
The above only is a preferred implementation of the present invention; should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the principle of the invention; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (10)
1. micro-channel heat exchanger comprises:
Two collector tubes, the homonymy end of two collector tubes is respectively arranged with import and outlet;
Some flat tubes are successively set between two collector tubes along the length direction of collector tube, and each flat tube has several through flow holes and is communicated with two collector tubes respectively; With
Several fins are arranged between the adjacent flat tube; It is characterized in that,
The flat tube flow resistance is the trend that reduces gradually by import and export place to the import and export place away from collector tube near collector tube and changes.
2. micro-channel heat exchanger according to claim 1 is characterized in that the variation of flat tube flow resistance is specially the variation of flat tube circulation area.
3. micro-channel heat exchanger according to claim 2, it is characterized in that, along the length direction of collector tube, described some flat tubes are divided into some groups, and the through-flow aperture of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube and changes.
4. micro-channel heat exchanger according to claim 2 is characterized in that, the through-flow aperture of every described flat tube is the trend that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube and changes.
5. micro-channel heat exchanger according to claim 2, it is characterized in that, along the length direction of collector tube, described some flat tubes are divided into some groups, and the width of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube to be changed.
6. micro-channel heat exchanger according to claim 2 is characterized in that, the width of every described flat tube is the trend that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube to be changed.
7. micro-channel heat exchanger according to claim 2, it is characterized in that, along the length direction of collector tube, described some flat tubes are divided into some groups, and the thickness of every group of flat tube is the trend that increases gradually by import and export place to the import and export place away from collector tube near collector tube to be changed.
8. micro-channel heat exchanger according to claim 2 is characterized in that, the thickness of every described flat tube is the trend that increases gradually by import and export place to the import and export place away from the collection liquid line near collector tube to be changed.
9. micro-channel heat exchanger according to claim 1, it is characterized in that, length direction along collector tube, described some flat tubes are divided into some groups, and the distance in every group of flat tube between adjacent two flat tubes is the trend that reduces gradually by import and export place to the import and export place away from collector tube near collector tube and changes.
10. micro-channel heat exchanger according to claim 1 is characterized in that, the distance between adjacent two flat tubes is the trend that reduces gradually by import and export place to the import and export place away from the collection liquid line near collector tube and changes.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910131244A CN101858698A (en) | 2009-04-10 | 2009-04-10 | Microchannel heat exchanger |
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|---|---|---|---|
| CN200910131244A CN101858698A (en) | 2009-04-10 | 2009-04-10 | Microchannel heat exchanger |
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Cited By (20)
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| CN101957105A (en) * | 2010-10-19 | 2011-01-26 | 广东美的制冷设备有限公司 | Heat exchanger for improving drainage performance |
| CN102095283A (en) * | 2011-01-25 | 2011-06-15 | 广东美的电器股份有限公司 | Micro-channel parallel flow heat exchanger of air conditioner |
| CN102269486A (en) * | 2011-07-12 | 2011-12-07 | 广东美的电器股份有限公司 | Parallel flow heat exchanger and room air conditioner |
| WO2014032488A1 (en) * | 2012-08-30 | 2014-03-06 | Yu Shaoming | Heat exchanger for micro channel |
| CN105299963A (en) * | 2015-11-30 | 2016-02-03 | 惠州学院 | Parallel flow heat exchanger |
| CN105674629A (en) * | 2016-04-13 | 2016-06-15 | 珠海格力电器股份有限公司 | Microchannel heat exchanger and heat-pump water heater |
| CN106123627A (en) * | 2016-07-05 | 2016-11-16 | 安徽天大电子科技股份有限公司 | A kind of air-conditioning heat exchanger |
| CN106288522A (en) * | 2015-05-25 | 2017-01-04 | 杭州三花微通道换热器有限公司 | Heat-exchanger rig and the heat pump with it |
| CN106662407A (en) * | 2014-04-22 | 2017-05-10 | 泰坦X引擎冷却控股公司 | Heat exchanger comprising a core of tubes |
| WO2018040036A1 (en) * | 2016-08-31 | 2018-03-08 | 合肥美的电冰箱有限公司 | Micro-channel heat exchanger and air-cooled refrigerator |
| WO2018040037A1 (en) * | 2016-08-31 | 2018-03-08 | 合肥美的电冰箱有限公司 | Micro-channel heat exchanger and air-cooled refrigerator |
| WO2018040034A1 (en) * | 2016-08-31 | 2018-03-08 | 合肥美的电冰箱有限公司 | Micro-channel heat exchanger and air-cooled refrigerator |
| WO2018040035A1 (en) * | 2016-08-31 | 2018-03-08 | 合肥美的电冰箱有限公司 | Micro-channel heat exchanger and air-cooled refrigerator |
| WO2018133735A1 (en) * | 2017-01-18 | 2018-07-26 | 上海冰鑫科技有限公司 | Brazed plate-and-shell type evaporator and manufacturing method thereof |
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| CN109000488A (en) * | 2017-09-14 | 2018-12-14 | 华北电力大学 | A kind of dot matrix heat exchanger |
| CN110567195A (en) * | 2019-09-04 | 2019-12-13 | 浙江富源制冷设备股份有限公司 | liquid separation head type microchannel without thermal resistance and manufacturing method thereof |
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| CN101957105A (en) * | 2010-10-19 | 2011-01-26 | 广东美的制冷设备有限公司 | Heat exchanger for improving drainage performance |
| CN102095283A (en) * | 2011-01-25 | 2011-06-15 | 广东美的电器股份有限公司 | Micro-channel parallel flow heat exchanger of air conditioner |
| CN102269486A (en) * | 2011-07-12 | 2011-12-07 | 广东美的电器股份有限公司 | Parallel flow heat exchanger and room air conditioner |
| US10436483B2 (en) | 2012-08-30 | 2019-10-08 | Shaoming Yu | Heat exchanger for micro channel |
| WO2014032488A1 (en) * | 2012-08-30 | 2014-03-06 | Yu Shaoming | Heat exchanger for micro channel |
| CN106662407A (en) * | 2014-04-22 | 2017-05-10 | 泰坦X引擎冷却控股公司 | Heat exchanger comprising a core of tubes |
| CN106288522B (en) * | 2015-05-25 | 2019-02-01 | 杭州三花微通道换热器有限公司 | Heat-exchanger rig and heat pump system with it |
| CN106288522A (en) * | 2015-05-25 | 2017-01-04 | 杭州三花微通道换热器有限公司 | Heat-exchanger rig and the heat pump with it |
| CN105299963A (en) * | 2015-11-30 | 2016-02-03 | 惠州学院 | Parallel flow heat exchanger |
| CN108603703B (en) * | 2016-02-02 | 2020-12-11 | 爱信精机株式会社 | Absorption heat pump device |
| US10857855B2 (en) | 2016-02-02 | 2020-12-08 | Aisin Seiki Kabushiki Kaisha | Absorption heat pump device |
| CN108603703A (en) * | 2016-02-02 | 2018-09-28 | 爱信精机株式会社 | Absorption heat pump unit |
| CN105674629A (en) * | 2016-04-13 | 2016-06-15 | 珠海格力电器股份有限公司 | Microchannel heat exchanger and heat-pump water heater |
| CN106123627A (en) * | 2016-07-05 | 2016-11-16 | 安徽天大电子科技股份有限公司 | A kind of air-conditioning heat exchanger |
| WO2018040035A1 (en) * | 2016-08-31 | 2018-03-08 | 合肥美的电冰箱有限公司 | Micro-channel heat exchanger and air-cooled refrigerator |
| WO2018040034A1 (en) * | 2016-08-31 | 2018-03-08 | 合肥美的电冰箱有限公司 | Micro-channel heat exchanger and air-cooled refrigerator |
| WO2018040037A1 (en) * | 2016-08-31 | 2018-03-08 | 合肥美的电冰箱有限公司 | Micro-channel heat exchanger and air-cooled refrigerator |
| WO2018040036A1 (en) * | 2016-08-31 | 2018-03-08 | 合肥美的电冰箱有限公司 | Micro-channel heat exchanger and air-cooled refrigerator |
| WO2018133735A1 (en) * | 2017-01-18 | 2018-07-26 | 上海冰鑫科技有限公司 | Brazed plate-and-shell type evaporator and manufacturing method thereof |
| CN109000488A (en) * | 2017-09-14 | 2018-12-14 | 华北电力大学 | A kind of dot matrix heat exchanger |
| CN109000488B (en) * | 2017-09-14 | 2024-05-28 | 华北电力大学 | Dot matrix heat exchanger |
| CN110567195A (en) * | 2019-09-04 | 2019-12-13 | 浙江富源制冷设备股份有限公司 | liquid separation head type microchannel without thermal resistance and manufacturing method thereof |
| CN110567195B (en) * | 2019-09-04 | 2023-09-26 | 浙江富源制冷设备股份有限公司 | Liquid head type micro-channel without heat resistance and manufacturing method thereof |
| WO2022007956A1 (en) * | 2020-07-10 | 2022-01-13 | 杭州三花微通道换热器有限公司 | Heat exchange assembly and heat exchange system having same |
| WO2022011570A1 (en) * | 2020-07-14 | 2022-01-20 | 杭州三花微通道换热器有限公司 | Heat exchanger |
| EP4184084A4 (en) * | 2020-07-14 | 2024-03-13 | Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd | Heat exchanger |
| CN113624043A (en) * | 2021-08-06 | 2021-11-09 | 合肥工业大学 | Temperature-equalizing distributed parallel micro-flow-channel heat exchanger and application thereof |
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