CN106322850A - Microchannel heat exchanger, refrigerator and air-cooled refrigerator - Google Patents
Microchannel heat exchanger, refrigerator and air-cooled refrigerator Download PDFInfo
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- CN106322850A CN106322850A CN201610796976.3A CN201610796976A CN106322850A CN 106322850 A CN106322850 A CN 106322850A CN 201610796976 A CN201610796976 A CN 201610796976A CN 106322850 A CN106322850 A CN 106322850A
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- heat exchanger
- fin
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- exchanger tube
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
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- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/02—Details of evaporators
- F25B2339/023—Evaporators consisting of one or several sheets on one face of which is fixed a refrigerant carrying coil
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- 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, a refrigerator and an air-cooled refrigerator. The microchannel heat exchanger comprises two header pipes, multiple heat exchange pipes and fins. The two header pipes are arranged in parallel. The two ends of the multiple heat exchange pipes are connected with the two header pipes correspondingly. The multiple heat exchange pipes are bent in the length direction to form multiple pipe layers. The refrigerant circulation resistance of some heat exchange pipes is smaller than that of the rest of the heat exchange pipes. Each fin is arranged between every two adjacent pipe layers or arranged on the outer side of the outermost pipe layer. In the extending direction of the heat exchange pipes, each fin extends in a corrugate shape. In the extending direction of the heater pipes, each fin continuously extends. The fins are provided with air holes. According to the microchannel heat exchanger, the problem that a large amount of water is attached to fin surfaces and cannot be thoroughly drained is solved, and the phenomenon that dense ice is produced on the surface of the microchannel heat exchanger, and therefore heat exchange efficiency is affected can be prevented. In addition, the defrosting period can be prolonged, the refrigerant flow of the multiple heat exchange pipes is promoted to be uniform, and heat exchange performance is improved.
Description
Technical field
The present invention relates to refrigeration and heat dissipation equipment field, especially relate to a kind of micro-channel heat exchanger and refrigerator, air-cooled ice
Case.
Background technology
Development on Thermal Performance of Micro Channels engineering stems from high-density electronic device cooling and microelectromechanical systems passes
The demand of heat, due to its compact conformation, heat exchange efficiency height, on domestic market, microchannel obtains in air conditioning for automobiles industry at first
Industrialized development.
The refrigeration system applying the natural coolant CO2 of a new generation is supercritical steam cycle, and system pressure is the highest.Such as at air-conditioning
In system, system high pressure operating pressure will be to more than 13MPa, and design pressure 42.5MPa to be reached, this is to compressor and heat exchanger
Resistance to pressure all propose the highest requirement.On the premise of compact conformation, micro-channel condenser can meet simultaneously resistance to pressure,
Durability and security of system.Along with production technology improves, micro-channel heat exchanger is increasingly becoming the favorite of heat exchanger circle, application row
Industry gets more and more.Owing to present refrigerator plot ratio requires more and more higher, refrigerator uses micro-channel evaporator to become refrigerator Developing Tendency
One of gesture.
Common micro-channel evaporator fin clearance is less, and finned length is less, is applied in refrigerator there is frost layer
Accumulating rate is too fast, and frost layer easily blocks fin clearance, causes that refrigerator defrost interval time is short, defrost is frequent.Defrost simultaneously
In journey shorter due to fin, on fin, moisture is not easy to be accumulated into and drips drippage, causes defrosting water to be difficult to drain, finally at vaporizer
Surface forms stupid ice, affects heat transfer effect.
Summary of the invention
It is contemplated that one of technical problem solved the most to a certain extent in correlation technique.To this end, the present invention
Individual aspect is directed to a kind of micro-channel heat exchanger, and this micro-channel heat exchanger easily drains defrosting water when defrosting.
A kind of refrigerator with above-mentioned micro-channel heat exchanger of offer and wind cooling refrigerator are provided.
According to the micro-channel heat exchanger of the present invention, including: two headers, said two header be arranged in parallel；Multiple
Heat exchanger tube, the two ends of the plurality of heat exchanger tube connect said two header respectively, and the plurality of heat exchanger tube is along its length
Being bent to form multiple tube layer, the cold-producing medium circulating resistance of the described heat exchanger tube of part is less than the cold-producing medium circulation of remaining described heat exchanger tube
Resistance；At least one fin, each described fin is located between adjacent two described tube layer or is located at outermost described tube layer
Outside, each corrugated extension of described fin on the bearing of trend of described heat exchanger tube, in the extension side of described header
The most each described fin extends continuously, and heat exchange described at least two in the described tube layer at each described fin and its place
Pipe is connected, and described fin is provided with air vent.
Micro-channel heat exchanger according to embodiments of the present invention, by arranging in the outside of adjacent tube layer or outermost tube layer
Fin, the corrugated extension of each fin on the bearing of trend of heat exchanger tube, on the bearing of trend of header, each fin is even
Reneing and stretch, thus micro-channel heat exchanger is during defrosting, fin surface frosted water can be accumulated into water droplet, and water droplet can be along continuous print
Fin landing swimmingly is also drained, and solves fin surface and hangs the problem that the water yield is relatively big, cannot drain, can prevent Thermal Performance of Micro Channels
Device surface produces stupid ice and affects heat exchange efficiency.By arranging air vent on fin, promote fin various location air phase
Flowing mutually, other regions preventing fin local gap from being caused by frost layer blocking do not have air to circulate, thus increase heat exchanger
Overall heat exchange amount.By being designed to less by the circulating resistance of part heat exchanger tube, this heat exchanger tube may be provided at micro-channel heat exchanger
Locate the most windward, thus promote the refrigerant flow of multiple heat exchanger tube uniform, improve heat exchanger overall heat exchange amount.
In certain embodiments, described air vent is located at adjacent two described flat tubes of described tube layer at described fin place
Between gap.So it is possible not only to connect the space of same tube layer by air vent, moreover it is possible to by different tube layer
Space connection is got up, and enables the air of heat exchanger diverse location to be sufficiently mixed further so that wind pushing temperature is more uniform.
In certain embodiments, on the bearing of trend of described header, the size of described air vent is 15-18 millimeter,
Being perpendicular to the size of described air vent on the bearing of trend of described header is 4-7 millimeter.
In certain embodiments, the pipe range of the described heat exchanger tube of part is less than the pipe range of remaining described heat exchanger tube.
Specifically, on the bearing of trend of described header, the pipe range of the plurality of heat exchanger tube is incremented by successively or passs successively
Subtract, and two the most adjacent described heat exchanger tubes are positioned at the pipe range of heat exchanger tube of windward side less than the heat exchanger tube being positioned at leeward side
Pipe range.Thus, the pipe range difference of the heat exchanger tube by each layer cold-producing medium is set, reduces each layer heat exchanger tube droop loss difference,
It is finally reached and promotes cold-producing medium separatory in multiple heat exchanger tubes uniform further, thus improve heat exchanger overall heat exchange further
Amount.
In further embodiments, the area of passage of the described heat exchanger tube of part is more than the flow-passing surface of remaining described heat exchanger tube
Long-pending.
Specifically, on the bearing of trend of described header, the area of passage of the plurality of heat exchanger tube is incremented by successively or depends on
Secondary successively decrease, and two the most adjacent described heat exchanger tubes are positioned at the area of passage of heat exchanger tube of windward side more than being positioned at leeward side
The area of passage of heat exchanger tube.Thus, the area of passage difference of the heat exchanger tube by each layer cold-producing medium is set, reduces each layer heat exchange
Tube voltage drop loss difference, is finally reached and promotes cold-producing medium separatory in multiple heat exchanger tubes uniform further, thus improve further
Heat exchanger overall heat exchange amount.
In certain embodiments, at least one described fin includes the first fin section and the second fin section, at described afflux
On the bearing of trend of pipe, the size of described first fin section is more than the size of described second fin section.Thus, air can be easily
It is blown between the inner tube layer of micro-channel heat exchanger, increases the distribution space of frost layer, reduce fin bottom portion frost layer accumulated amount
And speed, reduce the frosting performance impact to micro-channel heat exchanger, extend the defrost cycle.
According to the refrigerator of one aspect of the invention, including according to the micro-channel heat exchanger described in the above embodiment of the present invention.
Refrigerator according to embodiments of the present invention, by arranging above-mentioned micro-channel heat exchanger, beneficially during defrost, microchannel is changed
On hot device, defrosting water drains, and prevents micro-channel heat exchanger surface from producing stupid ice and affecting heat exchange efficiency.
Wind cooling refrigerator according to a further aspect of the present invention, limits refrigeration compartment and air channel, institute in described wind cooling refrigerator
State air channel and have for the return air inlet from described refrigeration compartment air intake, described wind cooling refrigerator include according to the present invention above-mentioned described in
Fin includes the first fin section and the micro-channel heat exchanger described in all embodiments of the second fin section, described micro-channel heat exchanger
Being located in described air channel, said two header is vertically arranged, and the described second fin section of described fin is arranged on described return air
The top of mouth.
Wind cooling refrigerator according to embodiments of the present invention, by arranging above-mentioned micro-channel heat exchanger, increases the distribution of frost layer
Space, reduces fin bottom portion frost layer accumulated amount and speed, reduces the frosting performance impact to micro-channel heat exchanger, prolongationization
The frost cycle.
The additional aspect of the present invention and advantage will part be given in the following description, and part will become from the following description
Obtain substantially, or recognized by the practice of the present invention.
Accompanying drawing explanation
Above-mentioned and/or the additional aspect of the present invention and advantage are from combining the accompanying drawings below description to embodiment and will become
Substantially with easy to understand, wherein:
Fig. 1 is the axonometric chart of micro-channel heat exchanger according to an embodiment of the invention.
Fig. 2 is the top view of the micro-channel heat exchanger shown in Fig. 1.
Fig. 3 is the axonometric chart of a kind of fin of micro-channel heat exchanger according to embodiments of the present invention.
Fig. 4 is the axonometric chart of the another kind of fin of micro-channel heat exchanger according to embodiments of the present invention.
Fig. 5 is to use the micro-channel heat exchanger sectional view of fin shown in Fig. 4.
Fig. 6 is that the Profile Correlation of three heat exchanger tubes of micro-channel heat exchanger according to an embodiment of the invention amplifies signal
Figure.
Fig. 7 is the top view of micro-channel heat exchanger in accordance with another embodiment of the present invention.
Fig. 8 is the sectional view in Fig. 7 along E-E direction.
Fig. 9 is the axonometric chart when fin is hidden of the micro-channel heat exchanger shown in Fig. 7.
Reference:
Micro-channel heat exchanger 100,
Header 1,
Heat exchanger tube 2, tube layer 20, pipeline section 21, flat segments 211, bending section the 212, first heat exchanger tube the 201, second heat exchanger tube
202, the 3rd heat exchanger tube 203, circulation passage 210,
Fin the 3, first fin section the 31, second fin section 32, air vent the 33, first air vent the 331, second air vent 332,
Parallel walls 301, vertical wall 302.
Detailed description of the invention
Embodiments of the invention are described below in detail, and the example of described embodiment is shown in the drawings, the most from start to finish
Same or similar label represents same or similar element or has the element of same or like function.Below with reference to attached
The embodiment that figure describes is exemplary, it is intended to is used for explaining the present invention, and is not considered as limiting the invention.
Below with reference to Fig. 1-Fig. 9, micro-channel heat exchanger 100 according to embodiments of the present invention is described.
Micro-channel heat exchanger 100 according to embodiments of the present invention, as depicted in figs. 1 and 2, micro-channel heat exchanger 100 includes:
Two headers 1, multiple heat exchanger tube 2 and at least one fin 3, two headers 1 be arranged in parallel.The two ends of multiple heat exchanger tubes 2
Connecting two headers 1 respectively, multiple heat exchanger tubes 2 (direction shown in arrow P in Fig. 1) along its length are bent to form multiple pipe
Layer 20.
Specifically, two headers 1 are arranged at distances from one another, and multiple heat exchanger tubes 2 are bent to form at least two-layer tube layer 20, each
Heat exchanger tube 2 is bent to form one or more pipeline section 21, is being parallel to the bearing of trend of header 1 (in Fig. 1 shown in arrow M just
To) on, one or more pipeline section 21 in the same plane constitutes a tube layer 20.Alternatively, multiple heat exchanger tube 2 is along arrow
The bearing of trend parallel interval of head header 1 shown in M is arranged.In the example illustrated in figure 1, multiple pipeline sections of each heat exchanger tube 2
21 all include flat segments 211 and the bending section between flat segments 211 212, and bending section 212 is around being parallel to prolonging of header 1
Stretch direction (direction shown in arrow M) and bend predetermined angular relative to flat segments 211.The angle of bend of the most each bending section 212
Degree is 180 degree, and the length of multiple heat exchanger tubes 2 is equal, and the number of times of multiple heat exchanger tubes 2 bending is equal, after the bending of multiple heat exchanger tubes 2
The length of the flat segments 211 formed is equal, and the length of the bending section 212 of formation is the most equal.Multiple heat exchanger tubes 2 be positioned at same row
Multiple flat segments 211 constitute a tube layer 20, when a certain layer tube layer 20 connect have fin 3 time, fin 3 can be connected to this
In tube layer 20 in the flat segments 211 of heat exchanger tube 2.
Alternatively, the cross-sectional profiles of heat exchanger tube 2 is the track type of two circular arc middle straight line, wherein, and heat exchanger tube 2 straight
Limit section is paralleled with the bearing of trend (direction shown in arrow M) of header 1, and fin 3 is connected with the straight section of heat exchanger tube 2.For side
Just describing, the heat exchanger tube 2 size on the bearing of trend (direction shown in arrow M) of header 1 is called the width of heat exchanger tube 2, claims
Heat exchanger tube 2 is being perpendicular to the width of heat exchanger tube 2 (direction shown in arrow M) and is being perpendicular to the length direction (arrow of heat exchanger tube 2
Direction shown in P) on the thickness that size is heat exchanger tube 2, the thickness direction of heat exchanger tube 2 is direction shown in arrow Q in Fig. 1.At Fig. 1
In, the width of heat exchanger tube 2 is more than the thickness of heat exchanger tube 2.
Specifically, each fin 3 is located between adjacent two tube layer 20 or is located at the outside of outermost tube layer 20, this
In, fin 3 can be one or more.In a concrete example of the present invention, as it is shown in figure 1, fin 3 is multiple, every phase
Being provided with a fin 3 between two adjacent tube layer 20, in multiple tube layer 20, the outside of outermost tube layer 20 is also respectively equipped with
Fin 3.The heat exchanger that micro-channel heat exchanger 100 is enumerated for multilamellar, heat exchanger is coupled together by each layer tube layer 20 of fin 3.
Specifically, the upper each corrugated extension of fin 3 of bearing of trend (direction shown in arrow P) at heat exchanger tube 2, at collection
The upper each fin 3 of the bearing of trend (direction shown in arrow M) of flow tube 1 extends continuously, and the tube layer 20 at each fin 3 and its place
In at least two heat exchanger tube 2 be connected.It is to say, fin 3 is corrugated on the length direction of heat exchanger tube 2, fin 3 is changing
Arrange continuously on the width of heat pipe 2.Arrange in continuous on the width of heat exchanger tube 2 referred to herein as fin 3, refer to
On the width of heat exchanger tube, after fin does not separates into multistage, interval is arranged, say, that fin is not on direction shown in M
It is interrupted.
It is understood that the fin of major part micro-channel heat exchanger is all short and small fin in prior art, fin is located at
Between adjacent two heat exchanger tubes, finned length is little, gap is the least, processed complex, makees frost layer accumulation when vaporizer uses under low temperature
Speed is fast, and during defrost, on fin, moisture is dispersed on each little fin, and steam is not easy to be accumulated into a drippage, difficulty drains.
And in the embodiment of the present invention by by fin 3 on the width (direction shown in arrow M) of heat exchanger tube 2 in continuously
Arranging, not only the processing of fin 3 is simplified, such as, can be processed into fin by the straight plate of whole piece, and processing cost is low, easily fills
Join, and when defrost the steam on fin 3 easily be gathered into drip and easily drain along continuous print fin 3 landing, it is to avoid frost layer
Form stupid ice on micro-channel heat exchanger 100 surface, thus ensure the heat transfer effect of micro-channel heat exchanger 100.
It addition, fin 3 is at least connected with two heat exchanger tubes 2 on the width of heat exchanger tube 2, with fin by multiple heat exchange
Pipe 2 links together, it is ensured that the structural strength of micro-channel heat exchanger 100.
Alternatively, all with the tube layer 20 at its place heat exchanger tubes 2 of each fin 3 are connected, the heat exchange being connected with fin 3
Pipe 2 can be linked into an integrated entity by fin 3, and sound construction is reliable.
In FIG, micro-channel heat exchanger 100 includes three heat exchanger tubes 2, forms four comb layers after three heat exchanger tube 2 bendings
20, this four combs layer 20 is linked together by three fins 3 between four comb layers 20, fin 3 adjacent in every comb layer 20
Together with being both connected to three heat exchanger tubes 2, the outside being positioned at outermost two tube layer 20 is also respectively equipped with a fin 3.This
In owing to tube layer 20 is along the spaced apart distribution in direction shown in arrow Q, therefore the outermost outer layer of tube layer 20 refers to multiple tube layer 20 and exists
Outermost along direction shown in Q.
With reference to Fig. 1, fin 3 is provided with air vent 33, so, after the air being blown into can pass fin 3 by air vent 33
It is blown between heat exchanger tube 2.So, air can be mutually mixed after flowing through outermost heat exchanger tube 2 or fin 3, a side
The problem that face causes top not have air to circulate after can solving to be blocked by frost layer because of some fin bottom portion gap, the most logical
Cross the air mixing flowing through heat exchanger diverse location so that wind pushing temperature is uniform, is favorably improved case temperature uniformity.
In embodiments of the present invention, the cold-producing medium circulating resistance of part heat exchanger tube 2 is less than the cold-producing medium stream of remaining heat exchanger tube 2
Logical resistance.
It is understood that when micro-channel heat exchanger runs, the heat exchanger tube of windward side because contacting at first with air return air,
Cold-producing medium is maximum with the extraneous air temperature difference, and therefore heat exchange amount is relatively big, heat exchange is more abundant.But in the most sufficient heat exchanger tube of heat exchange
Because two-phase section and superheat section are longer, cold-producing medium flow resistance is relatively big, in cold-producing medium assigning process, and the most sufficient heat exchanger tube of heat exchange
Refrigerant flow is less than normal on the contrary, and the feature bigger with heat exchange amount herein contradicts on the contrary.
And the cold-producing medium circulating resistance of part heat exchanger tube 2 is designed to less by the present invention, then this heat exchanger tube 2 is arranged
When micro-channel heat exchanger 100 runs can at first with the position of the air heat-exchange blown, cold-producing medium can be reduced and flow through this heat exchanger tube 2
Interior pressure drop, and then increase the refrigerant flow of this heat exchanger tube 2, so, the refrigerant flow that can promote multiple heat exchanger tube 2 is equal
Even, thus make cold-producing medium separatory in multiple heat exchanger tubes 2 uniform as far as possible, improve heat exchanger overall heat exchange amount.
Micro-channel heat exchanger 100 according to embodiments of the present invention, by adjacent tube layer 20 or outermost tube layer 20
Outside arranges fin 3, and each corrugated extension of fin 3 on the bearing of trend of heat exchanger tube 2, at the bearing of trend of header 1
Upper each fin 3 extends continuously, thus micro-channel heat exchanger 100 is during defrosting, and fin 3 surface frosted water can be accumulated into water
Drip, water droplet can along continuous print fin 3 landing swimmingly and drain, solve fin 3 surface hang that the water yield is relatively big, asking of cannot draining
Topic, can prevent micro-channel heat exchanger 100 surface from producing stupid ice and affecting heat exchange efficiency.By arranging air vent 33 on fin 3,
Promoting that fin various location air mutually flows, other regions preventing fin local gap from being caused by frost layer blocking are not free
Air-flow leads to, thus increases the overall heat exchange amount of heat exchanger.By the cold-producing medium circulating resistance of part heat exchanger tube 2 is designed to relatively
Little, this heat exchanger tube 2 may be provided at locating the most windward of micro-channel heat exchanger 100, thus promotes the cold-producing medium stream of multiple heat exchanger tube 2
Amount uniformly, improves heat exchanger overall heat exchange amount.
Be arranged to by the cold-producing medium circulating resistance of part heat exchanger tube 2 than other heat exchanger tubes 2 is little, has multiple method.
In certain embodiments, the pipe range of part heat exchanger tube 2 can be set smaller than the pipe range of remaining heat exchanger tube 2.Can
To understand, under same area of passage, the shortest then circulating resistance of heat exchanger tube 2 is the least, is set by the length difference alienation of heat exchanger tube 2
Meter, easily realizes circulating resistance during cold-producing medium circulation various heat exchange pipe different.
Specifically, on the bearing of trend (direction shown in arrow M) of header 1, the pipe range of multiple heat exchanger tubes 2 is incremented by successively
Or successively decrease successively, and in two the most adjacent heat exchanger tubes 2, be positioned at the pipe range of heat exchanger tube 2 of windward side less than being positioned at leeward side
The pipe range of heat exchanger tube 2.
Such micro-channel heat exchanger 100, sets the pipe range difference of the heat exchanger tube 2 by each layer cold-producing medium, reduces each
Layer heat exchanger tube droop loss difference, makes cold-producing medium flow through the resistance of each layer heat exchanger tube 2 essentially identical, is finally reached separatory uniform
Purpose, thus improve heat exchanger overall heat exchange amount further.
In a concrete example, heat exchanger tube 2 is three, on the bearing of trend of header 1, and the pipe of three heat exchanger tubes 2
Long ratio is 6:5:4.Wherein, the shortest heat exchanger tube 2 of pipe range is positioned at the windward side of heat exchanger, and the maximum heat exchanger tube 2 of pipe range is positioned at
The leeward side of heat exchanger.
In a concrete example, as shown in figs. 7 to 9, heat exchanger tube 2 is three, and micro-channel heat exchanger 100 is from bottom to top
Including: the first heat exchanger tube the 201, second heat exchanger tube 202 and the 3rd heat exchanger tube 203, the pipe range ratio of three heat exchanger tubes 2 is 4:5:6,
When wherein heat exchanger runs, air-flow blows to heat exchanger from below, and undermost first heat exchanger tube 201 is the longest, and the 3rd of the superiors changes
Heat pipe 203 is the shortest.
These three heat exchanger tube 2 has all bent three times and has formed four flat segments 211 and three bending sections 212, three heat exchanger tubes 2
Respective pipe range is made by the length adjusting respective flat segments 211.
Certainly, in the embodiment of the present invention, three heat exchanger tubes 2 are also by adjusting respective bending number of times, make respective pipe range
?.Such as, if the first heat exchanger tube 201 includes two flat segments 211 and a bending section 212, and the 3rd heat exchanger tube 203 is still
Including four flat segments 211 and three bending sections 212, the flat segments 211 of each heat exchanger tube 2 is the most isometric, now the first heat exchanger tube 201
Pipe range be about the half of pipe range of the 3rd heat exchanger tube 203.
It is understood that according to actual needs, the variable amounts of heat exchanger tube 2, the pipe range ratio of each heat exchanger tube 2 also may be used
Adapt to actual and change.
In further embodiments, the area of passage of part heat exchanger tube 2 can be designed larger than the mistake of remaining heat exchanger tube 2
Flow area.Being appreciated that under equal pipe range, the area of passage the biggest then cold-producing medium circulating resistance of heat exchanger tube 2 is the least, passes through
The area of passage differentiation design of heat exchanger tube 2, the most easily realizes circulating resistance during cold-producing medium circulation various heat exchange pipe different.
On the bearing of trend (direction shown in arrow M) of header 1, the area of passage of multiple heat exchanger tubes 2 successively be incremented by or
Person successively decreases successively, and in two the most adjacent heat exchanger tubes 2, the area of passage of the heat exchanger tube 2 being positioned at windward side is leeward more than being positioned at
The area of passage of the heat exchanger tube 2 of side.
Such micro-channel heat exchanger 100, sets the area of passage difference of the heat exchanger tube 2 by each layer cold-producing medium, subtracts
Little each layer heat exchanger tube droop loss difference, is finally reached and promotes cold-producing medium separatory in multiple heat exchanger tubes 2 uniform further, thus
Improve heat exchanger overall heat exchange amount further.
In a concrete example, as shown in figures 1 to 6, heat exchanger tube 2 is three, and micro-channel heat exchanger 100 is from bottom to top
Including: the first heat exchanger tube the 201, second heat exchanger tube 202 and the 3rd heat exchanger tube 203, the ratio of the area of passage of three heat exchanger tubes 2 is
4:3:2, when wherein heat exchanger runs, air-flow blows to heat exchanger from below, and the area of passage of undermost first heat exchanger tube 201 is
Greatly, the area of passage of the 3rd heat exchanger tube 203 of the superiors is minimum.
Specifically, as shown in Figure 6, the circulation passage 210, Ke Yigai of multiple cold-producing medium can be limited in each heat exchanger tube 2
Become the cross-sectional area size of circulation passage 210, the quantity etc. of circulation passage 210 in each heat exchanger tube 2, change each heat exchanger tube
The area of passage of 2 so that the pressure drop in heat transfer process of each stream is essentially identical, increases separatory uniformity as far as possible, improves heat-exchange performance
Energy.
It is understood that according to actual needs, the variable amounts of heat exchanger tube 2, the area of passage ratio of each heat exchanger tube 2
Also it is suitable for reality and changes.
In certain embodiments, air vent 33 is located at the sky between adjacent two flat tubes 2 of correspondence of fin 3 place tube layer 20
At gap.So it is possible not only to connect the space of same tube layer 20 by air vent 33, moreover it is possible to by the sky of different tube layer 20
Between connection get up, enable the air of heat exchanger diverse location to be sufficiently mixed further so that wind pushing temperature is more uniform.
Specifically, as it is shown in figure 5, size a of the upper air vent 33 of bearing of trend (direction shown in arrow M) at header 1
For 15-18 millimeter, on the bearing of trend being perpendicular to header 1, size b of air vent 33 is 4-7 millimeter.
As in Fig. 3, air vent 33 is square opening, length a of air vent 33 between 15-18 millimeter, the width of air vent 33
B is between 4-7 millimeter.Certainly, air vent 33 also can form other shapes, and air vent 33 may be designed as other sizes.
Specifically, as it is shown on figure 3, air vent 33 includes the first air vent 331 and the second air vent 332, the first air vent
331 is looping pit, and the second air vent 332 opens wide towards the side in direction shown in M.
In certain embodiments, as shown in figures 1 and 3, at the bearing of trend (direction shown in arrow P in Fig. 1) of heat exchanger tube 2
On, each fin 3 all include the parallel walls 301 being cross-linked and vertical wall 302 to form zigzag, parallel walls 301 and heat exchange
The bearing of trend of pipe 2 is parallel, and vertical wall 302 is perpendicular with the bearing of trend of heat exchanger tube 2.It is to say, parallel walls 301 is along side
Extending to P, vertical wall 302 extends along direction Q.When fin 3 is between adjacent two tube layer 20, parallel walls 301 is connected to
In tube layer 20, vertical wall 302 is clipped between two tube layer 20.Now, air vent 33 can be located on vertical wall 302, so may be used
Ensure ventilation effect, also will not reduce the contact area between heat exchanger tube 2 and fin 3 simultaneously, not interfere with heat exchanger tube 2 to fin
3 heat transfers.
Air vent 33 may be provided at the position discontiguous with heat exchanger tube 2 of fin 3, here to the structure of air vent 33,
Position is not restricted.Such as, when the outside of outermost layer tube layer 20 is provided with fin 3, on this fin 3, air vent 33 may be provided in vertically
On wall 302, it is possible to be located in parallel walls 301 discontiguous with tube layer 20.
In certain embodiments, as shown in Figure 4, at least one fin 3 includes the first fin section 31 and the second fin section 32,
Size h1 in bearing of trend (direction shown in arrow M) the upper first fin section 31 of header 1 is more than the chi of the second fin section 32
Very little h2.Fin 3 arranges to have length here and has short, be equivalent to be formed with breach on fin 3, the second fin section 32 to the first wing
The part above-mentioned breach of composition that fragment 31 is short, the setting of breach is that micro-channel heat exchanger 100 is carried out for frosting and defrost feature
The design structure optimized.
Specifically, when micro-channel heat exchanger 100 is used for exporting cold, air can be from corresponding micro-channel heat exchanger 100
This indentation, there blow to micro-channel heat exchanger 100.After absorbing cold due to air, humidity reduces, and the steam in air easily condenses
Frost layer is formed on the surface of micro-channel heat exchanger 100.And air is after indentation, there is dried, there is no the stop of fin 3 in indentation, there,
Air can easily be blown between the inner tube layer 20 of micro-channel heat exchanger 100, increases the distribution space of frost layer, reduces wing
Frost layer accumulated amount and speed bottom sheet 3, reduce the frosting performance impact to micro-channel heat exchanger 100, extends the defrost cycle.
Specifically, as shown in Figure 4, each fin 3 all includes at least two the first fin section 31 and/or at least two second
Fin section 32, on the bearing of trend (direction shown in arrow P) of heat exchanger tube 2, the first fin section 31 and the second fin section 32 are interlocked
Arrange.So arrange, on the one hand avoid fin 3 structural strength to reduce, on the other hand by spaced apart for breach on fin, the most micro-
Channel heat exchanger 100 is frost layer dispersion when frosting, thus can more quickly remove frost during defrost.
Further, when fin 3 is multiple, on multiple fins 3, the second fin section 32 is correspondingly arranged.It is to say, work as
When fin 3 is multiple, in the plane at tube layer 20 place, the projection of shape of multiple fins 3 is substantially the same, and each fin 3 all exists
Breach is formed at same position.The gap position of the most multiple fins 3 is consistent, thus is improving changing of micro-channel heat exchanger 100
While the thermal efficiency, the distribution space of frost layer can be increased further, reduce frost layer accumulated amount and speed bottom fin 3.
Alternatively, as shown in Figure 4, on the bearing of trend (direction shown in arrow M) of header 1, the second fin section 32
Size h2 is the 0.67-0.75 of size h1 of the first fin section 31, say, that second wing on the bearing of trend of header 1
The short 1/4-1/3 of fragment 32 to the first fin section 31.
If it is understood that the second fin section 32 is too short, it will weaken fin 3 at the second fin section 32 and tube layer
The bonding strength of 2, and if the second fin section 32 is long, again can to air formed hinder, the preferably second fin after considering
The 0.67-0.75 of size h1 that size h2 is the first fin section 31 of section 32, it is ensured that fin 3 all can smooth and easy dischargeization in full section
Frost water, when ensureing air intake, frost layer can be uniformly distributed simultaneously.
In certain embodiments, in each fin 3 first fin section 31 and the second fin section 32 all with the tube layer at its place
In 20, all heat exchanger tubes 2 are connected.
Owing to being spaced apart between adjacent two heat exchanger tubes 2, fin 3 after all heat exchanger tubes 2 being connected, on fin 3
Defrosting water will not fall centre heat exchanger tube 2 on, micro-channel heat exchanger 100 easily drains defrosting water.
Specifically, as it is shown in figure 5, along the bearing of trend (direction shown in arrow M) of header 1, the second fin section 32
Windward side and its place tube layer 20 on contact size m between outermost heat exchanger tube 2 be 5-10 millimeter.It is to say,
Even if fin 3 has been cooked breach setting, fin 3 is still joined with being formed to be connected between outermost heat exchanger tube 2 in the part of gap edge
Close.
Second fin section 32 is designed to contact size m between windward side and outermost heat exchanger tube 2 is 5-10 millimeter,
Ensureing that it is connected with outermost heat exchanger tube 2, when preventing fin 3 unsettled, on fin 3, water droplet can not change to outermost in following current
On heat pipe 2.
In certain embodiments, the tube layer 20 of micro-channel heat exchanger 100 is vertically arranged, and multiple tube layer 20 are in the horizontal direction
Spaced relation.Each the most corrugated extension of fin 3, each fin 3 extends the most continuously.Fin 3 is upper
Holding level with both hands neat, fin 3 forms breach in lower end, and fin 3 is divided into the first fin section 31 and the second fin section 32, wherein, the second fin
Contact height m between section 32 and the heat exchanger tube 2 of bottom is 5-10mm, shape between the heat exchanger tube 2 of fin 3 and bottom at this
Become interference fit.
Further, as it is shown in figure 1, on the bearing of trend (direction shown in arrow P) of heat exchanger tube 2, each fin 3 all in
Zigzag extends, and as shown in Figure 4, the gap n between adjacent teeth is 5-10 millimeter.Wherein, the basic phase of inter-lobe clearance n of fin 3
With, the ratio of the inter-lobe clearance n of each fin 3 is between 110%-90%.
To sum up, micro-channel heat exchanger 100 according to embodiments of the present invention, carry out according to frosting on heat exchanger and defrost feature
Optimize, by run through the fin 3 of multilamellar tube layer 20, fin 3 length difference alienation, at fin 3 surface perforate and various heat exchange pipe
The differentiation design of area of passage or pipe range, reduces the sensitivity that surface frost layer is gathered by parallel-flow heat exchanger heat exchange amount,
Slow down the impact that system is run by the accumulation of heat exchanger surface frost layer, the most beneficially defrosting water drains, and extends defrost as far as possible
In the cycle, promote heat exchange property.
Refrigerator (not shown) according to one aspect of the invention, changes including microchannel according to the above embodiment of the present invention
Hot device 100.Alternatively, micro-channel heat exchanger 100 can be used as the cold room of refrigerator or the vaporizer of temperature-changing chamber, Thermal Performance of Micro Channels
The structure of device 100 is illustrated by above-described embodiment, repeats no more here.
Refrigerator according to embodiments of the present invention, by arranging above-mentioned micro-channel heat exchanger 100, beneficially microchannel during defrost
On heat exchanger 100, defrosting water drains, and prevents micro-channel heat exchanger 100 surface from producing stupid ice and affecting heat exchange efficiency.
Wind cooling refrigerator (not shown) according to a further aspect of the present invention, limits refrigeration compartment and wind in wind cooling refrigerator
Road, air channel has for the return air inlet from refrigeration compartment air intake, and wind cooling refrigerator includes including according to the fin 3 that the present invention is above-mentioned
The micro-channel heat exchanger 100 of all embodiments of one fin section 31 and the second fin section 32.
The structure of micro-channel heat exchanger 100 is illustrated by above-described embodiment, repeats no more here.Micro-channel heat exchanger 100
Can be used as the cold room of wind cooling refrigerator or the vaporizer of temperature-changing chamber, micro-channel heat exchanger 100 is located in air channel, Thermal Performance of Micro Channels
Device 100 can be in the return air inlet of cold room or temperature-changing chamber the second shorter fin section 32 arranged above, and other location arrangements are longer
The first fin section 31.
Specifically, micro-channel heat exchanger 100 in air channel, two headers 1 are vertically arranged, the second fin section of fin 3
32 tops being arranged on return air inlet.That is wind cooling refrigerator is when refrigeration, and refrigeration chamber air blows to air channel from return air inlet,
The wind being blown into is blown into micro-channel heat exchanger 100 from the bottom of micro-channel heat exchanger 100.
Fin 3 is equivalent to breach in the part that the second fin section 32 to the first fin section 31 is short, and air can be micro-logical from correspondence
This indentation, there of road heat exchanger 100 blows to micro-channel heat exchanger 100.After air absorbs cold, humidity reduces, the steam in air
The surface easily condensing in micro-channel heat exchanger 100 forms frost layer.Owing to air blows to micro-channel heat exchanger 100 from indentation, there,
After indentation, there does not has the stop of fin 3, air can easily be blown between the inner tube layer 20 of micro-channel heat exchanger 100, increases
The big distribution space of frost layer, reduces frost layer accumulated amount and speed bottom fin 3, reduces frosting to micro-channel heat exchanger
The performance impact of 100, extends the defrost cycle.
Specifically, the horizontal width of horizontal width w (indicating in Fig. 3) the generally return air inlet of the second fin section 32
1.1-1.4 times, so, fin 3 can be made to avoid return air inlet as far as possible, facilitate return air to blow to the inside of micro-channel heat exchanger 100.
Further, when the outermost tube layer 20 of micro-channel heat exchanger 100 is provided with fin 3, micro-channel heat exchanger
The 100 direct naked leakages of outermost fin 3, and protect without backplate outside fin 3.It is to say, outermost fin 3 not with other
Parts are connected, and do not have protective equipment, contacts with the case gallbladder of refrigeration compartment and the cover plate of heat exchanger reducing it, and reduction casing leaks
Cold and the possibility of heat exchanger lid surface frosting.
Wind cooling refrigerator according to embodiments of the present invention, changes by arranging the microchannel exclusively for the design of single cycle wind cooling refrigerator
Hot device, has the following characteristics that
1. use whole piece plain fin that heat exchanger tube tube layer parallel for 3-4 layer is connected to one piece, reduce wing during defrost
Sheet surface hangs the water yield, prevents heat exchanger surface from forming " stupid ice "；
The most adjacent two sections of fin Length Ratios are between 75%-67%, it is possible to increase exchanger base windward side fin clearance,
Reduce frost layer accumulation to refrigerator air output and the impact of wind pushing temperature, prolongation defrost time；
3., by shortening finned length above cold room and temperature-changing chamber return air inlet, reduce and accumulate away from return air inlet frost layer the most nearby
Speed, reduces frost layer accumulation to cold room and the impact of temperature-changing chamber, prolongation defrost time；
4. fin 3 lower limb stretches into or stretches out the heat exchanger tube 5-10mm closed on, it is simple to defrosting water, to dirty, prevents water droplet
Gather at fin end portion；
5. the fin 3 surface perforate between adjacent two layers heat exchanger tube 2 so that air can prevent because of frost layer with horizontal mobility
Blocking bottom fin gap causes top not have air to flow through fin 3, reduces frosting heat exchanger heat exchange impact；
6., in order to alleviate because heat exchanger tube contacts successively with return air, cause each layer heat exchange pipeline flow resistance different, cause micro-
Bottom channel heat exchanger, refrigerant flow is less than normal, and micro-channel heat exchanger can not be confiscated and be played the phenomenon of high efficient heat exchanging, and the present invention is real
Execute the example area of passage by augmenting portion heat exchanger tube or flow path length, pass through the cold-producing medium of each heat exchanger tube as far as possible
Flow is identical, alleviates the phenomenon that heat exchanger separatory is uneven, improves the heat exchange amount of heat exchanger；
7. the direct naked leakage of both sides fin 3, unprotected layer, reinforcing plate or gripper shoe, reduces protective layer and contacts with case gallbladder
The cold draining brought and heat exchanger cover plate frosting may；
8 these designs solve micro-channel heat exchanger 100 and use present in wind cooling refrigerator evaporator heat exchange effect to table
Face frosting degree increase more sensitive issue, gives full play to parallel-flow heat exchanger feature, increases refrigerator plot ratio.
The parts etc. of other refrigeration systems such as compressor, condenser, refrigerant system configurations it is additionally provided with in being appreciated that refrigerator
And operation principle has been prior art, additionally the micro-channel heat exchanger 100 attachment structure in the refrigeration system of refrigerator is the most
Prior art, repeats no more here.
In describing the invention, it is to be understood that term " " center ", " longitudinally ", " laterally ", " length ", " width ",
" thickness ", " highly ", " on ", D score, "front", "rear", "left", "right", " vertically ", " level ", " top ", " end ", " interior ", " outward "
Deng instruction orientation or position relationship be based on orientation shown in the drawings or position relationship, be for only for ease of description the present invention with
Simplify and describe rather than indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration
And operation, therefore it is not considered as limiting the invention.
Additionally, term " first ", " second " are only used for describing purpose, and it is not intended that instruction or hint relative importance
Or the implicit quantity indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can express or
Implicitly include one or more this feature.In describing the invention, except as otherwise noted, " multiple " are meant that two
Individual or two or more.
In describing the invention, unless otherwise clearly defined and limited, term " install ", " being connected ", " connection ",
" fix " and should be interpreted broadly, connect for example, it may be fixing, it is also possible to be to removably connect, or integral；Can be machinery
Connect, it is also possible to be electrical connection；Can be to be joined directly together, it is also possible to be indirectly connected to by intermediary, can be two elements
Internal connection or the interaction relationship of two elements.For the ordinary skill in the art, can be with concrete condition
Understand above-mentioned term concrete meaning in the present invention.
In the description of this specification, the description of reference term " embodiment ", " example " etc. mean to combine this embodiment or
Specific features, structure, material or feature that example describes are contained at least one embodiment or the example of the present invention.At this
In description, the schematic representation of above-mentioned term is not necessarily referring to identical embodiment or example.And, description concrete
Feature, structure, material or feature can combine in any one or more embodiments or example in an appropriate manner.
Although an embodiment of the present invention has been shown and described, it will be understood by those skilled in the art that: not
These embodiments can be carried out multiple change in the case of departing from the principle of the present invention and objective, revise, replace and modification, this
The scope of invention is limited by claim and equivalent thereof.
Claims (10)
1. a micro-channel heat exchanger, it is characterised in that including:
Two headers, said two header be arranged in parallel；
Multiple heat exchanger tubes, the two ends of the plurality of heat exchanger tube connect said two header respectively, and the plurality of heat exchanger tube is along it
Length direction is bent to form multiple tube layer, and the cold-producing medium circulating resistance of the described heat exchanger tube of part is less than the system of remaining described heat exchanger tube
Cryogen circulating resistance；
At least one fin, each described fin is located between adjacent two described tube layer or is located at outermost described tube layer
Outside, each corrugated extension of described fin on the bearing of trend of described heat exchanger tube, at the bearing of trend of described header
Upper each described fin extends continuously, and heat exchanger tube described at least two in the described tube layer at each described fin and its place
Being connected, described fin is provided with air vent.
Micro-channel heat exchanger the most according to claim 1, it is characterised in that described air vent is located at described fin place
Gap between adjacent two described flat tubes of described tube layer.
Micro-channel heat exchanger the most according to claim 1, it is characterised in that described on the bearing of trend of described header
The size of air vent is 15-18 millimeter, and on the bearing of trend being perpendicular to described header, the size of described air vent is 4-7 milli
Rice.
Micro-channel heat exchanger the most according to claim 1, it is characterised in that the pipe range of the described heat exchanger tube of part is less than remaining
The pipe range of described heat exchanger tube.
Micro-channel heat exchanger the most according to claim 4, it is characterised in that described on the bearing of trend of described header
The pipe range of multiple heat exchanger tubes is incremented by successively or successively decreases successively, and is positioned at changing of windward side in two the most adjacent described heat exchanger tubes
The pipe range of heat pipe is less than the pipe range of the heat exchanger tube being positioned at leeward side.
Micro-channel heat exchanger the most according to claim 1, it is characterised in that the area of passage of the described heat exchanger tube of part is more than
The area of passage of remaining described heat exchanger tube.
Micro-channel heat exchanger the most according to claim 6, it is characterised in that described on the bearing of trend of described header
The area of passage of multiple heat exchanger tubes is incremented by successively or successively decreases successively, and is positioned at windward side in two the most adjacent described heat exchanger tubes
The area of passage of heat exchanger tube more than the area of passage of heat exchanger tube being positioned at leeward side.
8. according to the micro-channel heat exchanger according to any one of claim 1-7, it is characterised in that at least one described fin bag
Including the first fin section and the second fin section, on the bearing of trend of described header, the size of described first fin section is more than described
The size of the second fin section.
9. a refrigerator, it is characterised in that include according to the micro-channel heat exchanger according to any one of claim 1-8.
10. a wind cooling refrigerator, limits refrigeration compartment and air channel in described wind cooling refrigerator, described air channel has for from described
The return air inlet of refrigeration compartment air intake, it is characterised in that described wind cooling refrigerator includes Thermal Performance of Micro Channels according to claim 8
Device, described micro-channel heat exchanger is located in described air channel, and said two header is vertically arranged, described second wing of described fin
Fragment is arranged on the top of described return air inlet.
Priority Applications (1)
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| CN201610796976.3A CN106322850A (en) | 2016-08-31 | 2016-08-31 | Microchannel heat exchanger, refrigerator and air-cooled refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610796976.3A CN106322850A (en) | 2016-08-31 | 2016-08-31 | Microchannel heat exchanger, refrigerator and air-cooled refrigerator |
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| CN106322850A true CN106322850A (en) | 2017-01-11 |
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| CN201610796976.3A Pending CN106322850A (en) | 2016-08-31 | 2016-08-31 | Microchannel heat exchanger, refrigerator and air-cooled refrigerator |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| 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 |
| 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 |
| 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 |
| 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 |
| CN108801008A (en) * | 2018-09-13 | 2018-11-13 | 西安热工研究院有限公司 | A kind of cross connection structural printing circuit board type heat exchanger core body |
| CN110595112A (en) * | 2019-10-30 | 2019-12-20 | 广东美的制冷设备有限公司 | Heat exchanger and air conditioner with same |
| WO2020089162A1 (en) * | 2018-10-29 | 2020-05-07 | BSH Hausgeräte GmbH | Micro-channel heat exchanger and refrigeration appliance |
| CN111457620A (en) * | 2020-01-09 | 2020-07-28 | 安徽威灵汽车部件有限公司 | Heat exchanger, heat exchange system, household appliance and vehicle |
| CN113654383A (en) * | 2021-07-28 | 2021-11-16 | 祥博传热科技股份有限公司 | High-efficiency heat exchanger for phase-change cooling system |
| CN115235149A (en) * | 2022-06-22 | 2022-10-25 | 西安交通大学 | Disc type micro-channel heat regenerator for low-temperature refrigerator or freezer and working method |
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| 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 |
| 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 |
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| CN110595112A (en) * | 2019-10-30 | 2019-12-20 | 广东美的制冷设备有限公司 | Heat exchanger and air conditioner with same |
| CN111457620A (en) * | 2020-01-09 | 2020-07-28 | 安徽威灵汽车部件有限公司 | Heat exchanger, heat exchange system, household appliance and vehicle |
| CN113654383A (en) * | 2021-07-28 | 2021-11-16 | 祥博传热科技股份有限公司 | High-efficiency heat exchanger for phase-change cooling system |
| CN115235149A (en) * | 2022-06-22 | 2022-10-25 | 西安交通大学 | Disc type micro-channel heat regenerator for low-temperature refrigerator or freezer and working method |
| CN115235149B (en) * | 2022-06-22 | 2023-10-31 | 西安交通大学 | Disk-type micro-channel heat regenerator for low-temperature refrigerator or freezer and working method |
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