CN107003073A - The micro channel heat exchanger of resistance to frost - Google Patents
The micro channel heat exchanger of resistance to frost Download PDFInfo
- Publication number
- CN107003073A CN107003073A CN201580064494.2A CN201580064494A CN107003073A CN 107003073 A CN107003073 A CN 107003073A CN 201580064494 A CN201580064494 A CN 201580064494A CN 107003073 A CN107003073 A CN 107003073A
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- China
- Prior art keywords
- heat
- exchange tube
- slab
- heat exchanger
- exchange
- Prior art date
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- 239000012530 fluid Substances 0.000 claims abstract description 21
- 238000005452 bending Methods 0.000 claims abstract description 14
- 239000007788 liquid Substances 0.000 claims description 25
- 239000000203 mixture Substances 0.000 claims description 12
- 238000010025 steaming Methods 0.000 claims description 5
- 239000003507 refrigerant Substances 0.000 description 27
- 238000005057 refrigeration Methods 0.000 description 9
- 238000007906 compression Methods 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000001816 cooling Methods 0.000 description 4
- 238000010257 thawing Methods 0.000 description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 239000002826 coolant Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005538 encapsulation Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 241001442589 Convoluta Species 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Classifications
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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
- F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
- F28F19/006—Preventing deposits of ice
-
- 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
- F28D1/0475—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 having a single U-bend
- F28D1/0476—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 having a single U-bend the conduits having a non-circular cross-section
-
- 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
- F28D1/053—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 straight
- F28D1/0535—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 straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
-
- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/02—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the heat-exchange media travelling at an angle to one another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- 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
- F28D2001/0253—Particular components
- F28D2001/026—Cores
- F28D2001/0266—Particular core assemblies, e.g. having different orientations or having different geometric features
-
- 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
- F28D2001/0253—Particular components
- F28D2001/026—Cores
- F28D2001/0273—Cores having special shape, e.g. curved, annular
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
- F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels
Abstract
There is provided a kind of heat exchanger, it includes the first manifold, the second manifold and fluidly couples multiple heat exchange pipeline sections of first manifold and second manifold.The heat exchange pipeline section includes limiting the bending section of the first slab arranged at an angle to each other and the second slab.Each in the heat exchange pipeline section includes at least the first heat-exchange tube and the second heat-exchange tube, and first heat-exchange tube and second heat-exchange tube are connected by the web extended in-between at least in part.First heat-exchange tube and second heat-exchange tube are asymmetric so that the cross-sectional flow area of first heat-exchange tube is different from the cross-sectional flow area of second heat-exchange tube.Fluid flows successively through first heat-exchange tube of first slab and second slab, and subsequently passes through second heat-exchange tube of second slab and first slab.
Description
Background technology
Present invention relates in general to heat pump and refrigeration application, and more specifically to being arranged to heat pump or system
The micro channel heat exchanger of cooling system.
Heating, ventilation, air-conditioning and refrigeration (HVAC＆R) system include heat exchanger, with the refrigerant circulation in system with
Excluded between environment or receive heat.Due to its compactedness, the rigidity of structure and excellent properties, increased popularity is a type of
Exchanger is microchannel or mini channel heat-exchanging.Micro channel heat exchanger includes two or more receiving forms, such as
Pipe, cooling or heating fluid (that is, refrigerant or ethylene glycol solution) are circulated by the receiving form.Pipe generally has flat
Section and multiple parallel flow channels.Generally, fin is arranged to extends between the tubes, to contribute in heating/cooling stream
Heat energy transmission is carried out between body and surrounding environment.Fin has wave pattern, is incorporated to air vent to increase heat transfer, and generally
Pipe is fixed to by soldering.
Conventional micro channel heat exchanger typically has substantially the same fin in whole heat exchanger core.In heat pump
In refrigeration application, when micro channel heat exchanger be used as evaporator when, be provided to heat exchanger be used for cool down air-flow in institute
The moisture of presence is condensable, and then freezes on outside heat-exchanger surface.The ice or frost of formation can be blocked by heat friendship
The air-flow of parallel operation, so as to reduce the efficiency and function of heat exchanger and HVAC ＆ R system.Micro channel heat exchanger than pipe and
Plate fin type heat exchanger tends to quickly freeze, and therefore needs frequent defrosting, so as to reduce useful heat exchange
Device utilizes time and overall performance.Exchanged therefore, it is desirable to build with improved resistance to frost and the micro channel heat of enhanced performance
Device.
The content of the invention
There is provided a kind of heat exchanger, it includes the first manifold, the second manifold and fluidly couples the first manifold and second
Multiple heat exchange pipeline sections of manifold.Heat exchange pipeline section includes limiting the curved of the first slab for arranging at an angle to each other and the second slab
Pars convoluta.Each in heat exchange pipeline section includes at least the first heat-exchange tube and the second heat-exchange tube, the first heat-exchange tube and the
Two heat-exchange tubes are connected by the web extended in-between at least in part.First heat-exchange tube and the second heat-exchange tube are not
Symmetrically so that the cross-sectional flow area of the first heat-exchange tube is different from the cross-sectional flow area of the second heat-exchange tube.Fluid according to
It is secondary to flow through the first heat-exchange tube of the first slab and the second slab, and subsequently pass through the second heat of the second slab and the first slab
Exchange pipe.
In addition to one or more of features described above, or alternatively, in a further embodiment, through heat
The air-flow of exchanger is moved from the first slab towards the second slab.
In addition to one or more of features described above, or alternatively, in a further embodiment, through heat
The air-flow of exchanger is moved from the second slab towards the first slab.
In addition to one or more of features described above, or alternatively, in a further embodiment, first is hot
The cross-sectional flow area for exchanging pipe is less than the area of section of the second heat-exchange tube.
In addition to said one or multiple features, or alternatively, in a further embodiment, the first heat exchange
Fluid in pipe includes the liquid or liquid vaporses mixture that contained steam is less than 20 mass %.
In addition to said one or multiple features, or alternatively, in a further embodiment, the second heat exchange
Fluid in pipe includes the steam or liquid vaporses mixture that contained steam is at least 50 mass %.
In addition to one or more of features described above, or alternatively, in a further embodiment, first is hot
The cross-sectional flow area for exchanging pipe is more than the area of section of the second heat-exchange tube.
In addition to said one or multiple features, or alternatively, in a further embodiment, the second heat exchange
Fluid in pipe includes the liquid or liquid vaporses mixture that contained steam is less than 20 mass %.
In addition to said one or multiple features, or alternatively, in a further embodiment, the first heat exchange
Fluid in pipe includes the steam or liquid vaporses mixture that contained steam is at least 50 mass %.
According to of the invention, another embodiment is there is provided a kind of heat exchanger again, and it includes the first manifold, the second manifold
Fluidly couple multiple heat exchange pipeline sections of the first manifold and the second manifold.Heat exchange pipeline section includes limiting cloth at an angle to each other
The first slab put and the bending section of the second slab.Each in heat exchange pipeline section includes at least the first heat-exchange tube and second
Heat-exchange tube, the first heat-exchange tube and the second heat-exchange tube are connected by the web extended in-between at least in part.Fluid
Flow successively through the first heat-exchange tube and the second heat-exchange tube of heat exchanger so that the fluid in the first heat-exchange tube is liquid,
And the fluid in the second heat-exchange tube is steam.
In addition to one or more of features described above, or alternatively, in a further embodiment, first is hot
It is asymmetric to exchange pipe and the second heat-exchange tube so that the cross-sectional flow area of the first heat-exchange tube is different from the second heat exchange
The cross-sectional flow area of pipe.
In addition to one or more of features described above, or alternatively, in a further embodiment, first is hot
The cross-sectional flow area for exchanging pipe is less than the area of section of the second heat-exchange tube.
In addition to one or more of features described above, or alternatively, in a further embodiment, through heat
The air-flow of exchanger is moved from the first slab towards the second slab.
In addition to one or more of features described above, or alternatively, in a further embodiment, wherein wearing
The air-flow of over-heat-exchanger is moved from the second slab towards the first slab.
Brief description of the drawings
The theme specifically noted and be distinctly claimed in claims at this specification ending is considered as
The present invention.The foregoing and other feature and advantage of the present invention is from the detailed description carried out below in conjunction with accompanying drawing it is clear that in accompanying drawing
In：
Fig. 1 is the schematic diagram of the example of the steam refrigerating circulation of refrigeration system；
Fig. 2 is the side view before bending operation according to the micro channel heat exchanger of embodiment of the present invention；
Fig. 3 is the sectional view of the pipeline section of the micro channel heat exchanger according to embodiment of the present invention；
Fig. 4 is the sectional view of the pipeline section of the micro channel heat exchanger according to embodiment of the present invention；
Fig. 5 is the perspective view of the micro channel heat exchanger according to embodiment of the present invention；
Fig. 6 is the sectional view of the micro channel heat exchanger according to another embodiment of the present invention；
Fig. 7 is the sectional view of the micro channel heat exchanger of the another embodiment according to the present invention；And
Fig. 8 is the sectional view of the micro channel heat exchanger of the another embodiment according to the present invention.
Refer to the attached drawing is described in detail by way of example to explain embodiment of the present invention and advantages and features.
It is described in detail
Referring now to Figure 1, it schematically shows the vapor compression refrigeration agent circulation 20 of air-conditioning system or refrigeration system.Show
Example property air-conditioning or refrigeration system include but is not limited to, such as separation, encapsulation, cooler, roof, supermarket and transport refrigeration system.
Refrigerant R is configured to cycle through vapor-compression cycle 20 so that heat is absorbed when cooling agent R is evaporated under low temperature and low pressure
Measure and discharge heat when being condensed under higher temperature and pressure.Herein in circulation 20, refrigerant R is with as shown by arrows inverse
Clockwise flows.Compressor 22 receive come flash-pot 24 refrigerant vapour and by the refrigerant vapor compression to compared with
High temperature and pressure, then relatively hot steam walk to condenser 26, in condenser 26 by with cooling medium (not
Show) heat exchange relationship of such as air and the steam is cooled down and condensed to liquid.Liquid refrigerant R is then from condenser
26 walk to expansion gear 28, and wherein refrigerant R can be expanded into the liquid/vapor shape of low temperature two-phase when walking to evaporator 24
State.Low-pressure steam is subsequently returned to compressor 22, and the circulation is repeated within compressor 22.It should be understood that the refrigeration that Fig. 1 describes is followed
Ring 20 is the simple expression of HVAC ＆ R system, and can be including in place of many enhancings known in the art and special in schematic diagram
Levy.Specifically, heat pump refrigerant circulation includes flowing the four-way valve (not shown) for being arranged on compressor downstream relative to refrigerant,
It allows the refrigerant flow direction in whole refrigerant circulation to invert, with for the environment that will be adjusted is in cooling and heats
Switch between operator scheme.
Referring now to Figure 2, illustrating in greater detail the example for the heat exchanger 30 being arranged in vapor compression system 20.
Heat exchanger 30 may be used as condenser 24 or evaporator 28 in vapor compression system 20.Heat exchanger 30 includes at least first
Manifold or collector 32, the second manifold or collector 34 that are spaced apart with the first manifold 32 and in the first manifold 32 and the second manifold
Extend and connect multiple pipeline sections 36 of the first manifold 32 and the second manifold 34 between 34 with parallel spaced relation.In the non-limit shown
In property embodiment processed, the first collector 32 and the second collector 34 are substantially horizontally oriented, and heat exchange pipeline section 36 is in two collection
Extended substantially vertically between pipe 32,34.However, other configurations, such as the first collector 32 and the second collector 34 are essentially perpendicularly
Arrangement, it is also within the scope of the invention.
As shown in Fig. 3 and Fig. 4 section, in the multiple pipeline sections 36 extended between the first manifold 32 and the second manifold 34
Each is multiport extruding (MPE) pipeline section 36, and including at least the first heat-exchange tube 38 and the second heat-exchange tube 40, it is described
First heat-exchange tube 38 and the second heat-exchange tube 40 are connected by the web 42 extended in-between at least in part.In an implementation
In scheme, being arranged in the web 42 at outermost pipeline section 36 includes multiple openings.
The internal flow passageway of each heat-exchange tube 38,40 can be divided into by inwall multiple discrete flow channel 44a,
44b, the multiple discrete flow channel 44a, 44b extend in the length of pipeline section 36 and corresponding first manifold 32 with
Set up and be in fluid communication between second manifold 34.The internal flow passageway of first heat-exchange tube 38 is segmented into and the second heat-exchange tube
The different discrete flow channel 44 of the quantity of 40 internal flow passageway.Flow channel 44a, 44b can have any shape
Section, such as circular cross-section, square-section, trapezoid cross section, triangular-section or another noncircular cross section.Including discrete flowing
Passage 44a, 44b multiple heat exchange pipeline sections 36 can use known technology to be formed, and such as extrude.
Each heat-exchange tube 40 of first heat-exchange tube 38 and second have corresponding leading edge 46a, 46b, trailing edge 48a, 48b,
First surface 50a, 50b and second surface 52a, 52b (Fig. 3).Leading edge 46a, 46b of each heat-exchange tube 38,40 is relative to logical
The air-flow A of over-heat-exchanger 30 is in its corresponding trailing edge 48a, 48b upstream.
First heat-exchange tube 38 and second heat exchanger pipe 40 are substantially different or asymmetric.In the non-limiting reality shown
Apply in scheme, the heat-exchange tube 38 of the second heat-exchange tube 40 to the first is wider and with greater number of discrete flow channel 44,
So as to cause bigger cross-sectional flow area.Although the heat-exchange tube 38 of the second heat-exchange tube 40 to the first as shown in Figure 3 is wider,
But other configurations, such as multiple first heat-exchange tubes 38 are than multiple second heat-exchange tubes 40 with bigger sectional flow face
Long-pending configuration, is within the scope of the invention.Dissymmetry ratio between first heat-exchange tube 38 and second heat exchanger pipe 40 can
With any one in the parameters depending on heat exchanger, such as capacity,
Referring now to Figure 5, each pipeline section 36 of heat exchanger 30 includes at least one bending section 60, so that heat exchanger 30
There is multi-pipeline configuration relative to air-flow A.Bending section 60 is generally formed around axis, and the axis is substantially perpendicular to pipeline section 36
Longitudinal axis or discrete flow channel 44a, 44b and extend.In the embodiment illustrated, bending section 60 is that band is folded
Portion；But other kinds of bending section is within.In the non-limiting embodiments shown, bending section 60
Formed at the approximate midpoint of pipeline section 36 between relative the first manifold 32 and the second manifold 34.
Bending section 60 at least partially defines the first section or the section of slab 62 and second or slab 64 of multiple pipeline sections 36.
As illustrated, bending section 60 can be formed such that the first slab is positioned relative to the second slab 64 with obtuse angle.Alternately or separately
Other places, bending section 60 can also be formed such that the first slab 62 is arranged at an acute angle or is basically parallel to the second slab 64.Bending section
60 allow to be formed the heat exchanger 30 with routine A coils or V coil shapes.In the first slab 62 and the second slab 64 substantially
In the embodiment of parallel arrangement, the length of the first slab 62 and the second slab 64 can change, to offset the phase of the first manifold 32
For the position of the second manifold 34.Alternately, the free end of the first slab 62 and the second slab 64 can at an angle to each other or
Open, to accommodate manifold 32,34.
As it was previously stated, heat exchanger 30 is configured due to the bending section 60 wherein formed including multi-pipeline.Shown in Fig. 6
In one embodiment, heat exchanger 30 is configured so that the He of first heat exchanger pipe 38 in the first slab 62 of pipeline section 36
Second heat exchanger pipe 40 limits the first pipeline both relative to air-flow A.Similarly, in the second slab 64 of same pipeline section 36
First heat exchanger pipe 38 and second heat exchanger pipe 40 limit follow-up pipeline both relative to air-flow.Although attached what is shown
In figure, fluid or refrigerant relative to the direction of air-flow there is adverse current to be orientated, but refrigerant has its of PARALLEL FLOW orientation
His embodiment is also within the scope of the invention.
In another embodiment, as shown in Figure 7 and Figure 8, in identical the first slab 62 or the second slab 64
First heat exchanger pipe 38 and second heat exchanger pipe 40 are configured as the difference in the refrigerant flowpath of heat exchanger 30
Pipeline.For example, as shown in fig. 7, heat exchanger 30 can be configured so that refrigerant is flowing through the second slab 64 and the first slab
Before 62 second heat exchanger pipe 40, the first heat exchanger pipe 38 of the first slab 62 and the second slab 64 is flowed successively through.So
And, other flow arrangements, such as shown in figure 8, refrigerant flows through the second heat friendship before first heat exchanger pipe 38 is flowed through
The situation of parallel operation pipe 40 is within the scope of the invention.In addition, as shown in Fig. 7 and Fig. 8 embodiment, refrigerant can with
Enter heat exchanger 30 at air-flow identical slab, or alternately, refrigerant can enter at the slab different from air-flow
Enter heat exchanger.
Direction according to air-flow A relative to heat exchanger 30, and which slab are configured to refrigerant and enter heat exchange
The entrance of device 30, the flowing through first heat exchanger pipe 38 has the first configuration, and passes through the second heat exchanger pipe 40
Flowing configured with different from the first configuration second.Shown in non-limiting embodiments as shown in Figure 7, air-flow A from
In the case that first slab 62 flows to the second slab 64, flowing in first heat exchanger pipe 38 parallel to air-flow A direction, and
And the flowing in second heat exchanger pipe 40 is opposite with air-flow A.As shown in figure 8, being first provided to the second heat friendship in refrigerant
In the embodiment of parallel operation pipe 40, flowing in second heat exchanger pipe 40 is parallel to air-flow A direction, and the first heat exchange
Flowing in device pipe 38 is opposite with air-flow A.
In order that white formation is minimized on heat exchanger 30, the flow path through the refrigerant of heat exchanger 30 can be with
The liquid or two-phase part for being configured so that refrigerant flow through the heat exchanger tube with small cross sections flow area, and make
The vapor portion of cryogen flows through the heat exchanger tube with larger cross-section flow area.For example, in the embodiment shown in Fig. 8
In, the cross-sectional flow area of second heat exchanger pipe 40 is smaller than first heat exchanger pipe 38.Air-flow is configured to from the first slab
62 flow to the second slab 64, and liquid or two-phase system cryogen are input into the second heat exchanger pipe 40 of the first slab 62.When
When refrigerant reaches the first heat-exchange tube 38 of the first slab 62, refrigerant is to be in the overheat steaming than saturation temperature higher temperature
Gas.Therefore, the amount of heat transfer occurred between air-flow A and the first heat-exchange tube 38 of the first slab 62 is restricted.Such
In embodiment, the steam of liquid or liquid vaporses mixture in the second heat-exchange tube 40 is less than 20 mass %, and first
The steam of steam or liquid vaporses mixture in heat exchanger tube 38 is at least 50 mass %.
In other embodiments, as shown in fig. 7, refrigerant can be provided to the first heat-exchange tube 38, then provide
To the second heat-exchange tube 40.In such embodiment, first heat exchanger pipe 38, which can have, is less than second heat exchanger pipe
40 cross-sectional flow area so that the steam of liquid or liquid vaporses mixture in the first heat-exchange tube 38 is less than 20 matter
The steam of steam or liquid vaporses mixture in amount %, and second heat exchanger pipe 40 is at least 50 mass %.
The presence of superheated vapor, and in the refrigerant tubing that air-flow initially contacts heat exchanger air-flow A and fluid R it
Between amount of heat transfer reduce, cause reduction white accumulation rate and improve frost resistance.Therefore, reduce frost formation and because
Defrosting cycle-index needed for this operating efficiency in order to maintain heat exchanger 30.Because (because the defrosting in the second slab is followed
Ring number of times reduce and heat transfer increase) heat exchanger 30 operating efficiency improve, so needed for desired application can also be reduced
Heat exchanger 30 size.Alternately, the size of miscellaneous part such as compressor can be reduced, this can then be produced even
Higher evaporating temperature and further reduce defrosting circulation and lifting system performance.
Although the present invention is particularly shown and described with reference to the exemplary as shown in the drawings,
It will be recognized to those skilled in the art that various modifications can be made without departing from the spirit and scope of the present invention.Cause
This, it is desirable to the disclosure is not limited to disclosed one or more particulars, but the disclosure will include falling in appended power
All embodiments in the range of profit requirement.Specifically, similar principle and ratio can expand to rooftop applications and vertical
Encapsulation unit.
Claims (14)
1. a kind of heat exchanger, it includes：
First manifold；
Second manifold, it is separated with first manifold；
Multiple heat exchange pipeline sections, it is with the arranged in parallel relation at interval and fluidly couples first manifold and described second
Manifold, the multiple heat exchange pipeline section includes the first slab and the bending section of the second slab for limiting the heat exchange pipeline section, institute
State the first slab and be arranged to angled with second slab, each in the multiple heat exchange pipeline section includes at least the
One heat-exchange tube and the second heat-exchange tube, first heat-exchange tube and second heat-exchange tube are at least partly by in-between
The web connection of extension, first heat-exchange tube and second heat-exchange tube are asymmetric so that first heat is handed over
The cross-sectional flow area for changing pipe is different from the cross-sectional flow area of second heat-exchange tube；
Wherein fluid be configured to flow successively through first heat-exchange tube of first slab, second slab it is described
First heat exchange of first heat-exchange tube, second heat-exchange tube of second slab and first slab
Pipe.
2. heat exchanger according to claim 1, wherein through the air-flow of the heat exchanger from the first slab court
Moved to second slab.
3. heat exchanger according to claim 1, wherein through the air-flow of the heat exchanger from the second slab court
Moved to first slab.
4. heat exchanger according to claim 1, wherein the cross-sectional flow area of first heat-exchange tube is less than
The area of section of second heat-exchange tube.
5. heat exchanger according to claim 4, wherein the fluid in first heat-exchange tube includes contained steaming
Gas is less than 20 mass % liquid or liquid vaporses mixture.
6. heat exchanger according to claim 4, wherein the fluid in second heat-exchange tube includes contained steaming
Gas is at least 50 mass % steam or liquid vaporses mixture.
7. heat exchanger according to claim 1, wherein the cross-sectional flow area of first heat-exchange tube is more than
The area of section of second heat-exchange tube.
8. heat exchanger according to claim 7, wherein the fluid in second heat-exchange tube includes contained steaming
Gas is less than 20 mass % liquid or liquid vaporses mixture.
9. heat exchanger according to claim 7, wherein the fluid in first heat-exchange tube includes contained steaming
Gas is at least 50 mass % steam or liquid vaporses mixture.
10. a kind of heat exchanger, it includes：
First manifold；
Second manifold, it is separated with first manifold；
Multiple heat exchange pipeline sections, it is with the arranged in parallel relation at interval and fluidly couples first manifold and described second
Manifold, the multiple heat exchange pipeline section includes the of the first section for limiting the heat exchanger pipeline section and the heat exchange pipeline section
The bending section of two sections, first section is arranged to be at an angle of with second section, each in the multiple pipeline section
It is individual including at least the first heat-exchange tube and the second heat-exchange tube, first heat-exchange tube and second heat-exchange tube at least portion
Divide and connected by the web extended in-between；
Wherein fluid is configured to flow successively through first heat-exchange tube and second heat-exchange tube of the heat exchanger,
So that the fluid in first heat-exchange tube is liquid, and the fluid in second heat-exchange tube is to steam
Gas.
11. heat exchanger according to claim 10, wherein first heat-exchange tube and second heat-exchange tube are
It is asymmetric so that the cross-sectional flow area of first heat-exchange tube is different from the sectional flow face of second heat-exchange tube
Product.
12. heat exchanger according to claim 11, wherein the cross-sectional flow area of first heat-exchange tube is small
In the area of section of second heat-exchange tube.
13. heat exchanger according to claim 10, wherein through the air-flow of the heat exchanger from first slab
Towards second slab movement.
14. heat exchanger according to claim 10, wherein through the air-flow of the heat exchanger from second slab
Towards first slab movement.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201462084752P | 2014-11-26 | 2014-11-26 | |
| US62/084752 | 2014-11-26 | ||
| PCT/US2015/061902 WO2016085817A2 (en) | 2014-11-26 | 2015-11-20 | Frost tolerant microchannel heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107003073A true CN107003073A (en) | 2017-08-01 |
Family
ID=54771215
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580064494.2A Pending CN107003073A (en) | 2014-11-26 | 2015-11-20 | The micro channel heat exchanger of resistance to frost |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20170356700A1 (en) |
| EP (1) | EP3224565B1 (en) |
| CN (1) | CN107003073A (en) |
| RU (1) | RU2693946C2 (en) |
| WO (1) | WO2016085817A2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110345799A (en) * | 2018-04-08 | 2019-10-18 | 浙江盾安热工科技有限公司 | Flat tube component and heat exchanger comprising the flat tube component |
| US20190376697A1 (en) * | 2018-06-08 | 2019-12-12 | Johnson Controls Technology Company | Over-bent coil arrangements for climate management systems |
| US11236946B2 (en) | 2019-05-10 | 2022-02-01 | Carrier Corporation | Microchannel heat exchanger |
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| US5279360A (en) * | 1985-10-02 | 1994-01-18 | Modine Manufacturing Co. | Evaporator or evaporator/condenser |
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| US20030102113A1 (en) * | 2001-11-30 | 2003-06-05 | Stephen Memory | Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle |
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| KR20080108545A (en) * | 2006-03-16 | 2008-12-15 | 베헤르 게엠베하 운트 콤파니 카게 | Heat exchanger for a motor vehicle |
| US10247481B2 (en) * | 2013-01-28 | 2019-04-02 | Carrier Corporation | Multiple tube bank heat exchange unit with manifold assembly |
| CN103411446B (en) * | 2013-08-28 | 2016-04-13 | 杭州三花微通道换热器有限公司 | Heat exchanger |
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2015
- 2015-11-20 EP EP15804285.3A patent/EP3224565B1/en active Active
- 2015-11-20 CN CN201580064494.2A patent/CN107003073A/en active Pending
- 2015-11-20 WO PCT/US2015/061902 patent/WO2016085817A2/en active Application Filing
- 2015-11-20 RU RU2017121846A patent/RU2693946C2/en active
- 2015-11-20 US US15/526,904 patent/US20170356700A1/en not_active Abandoned
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|---|---|---|---|---|
| DE3813339A1 (en) * | 1988-04-21 | 1989-11-09 | Happel Gmbh & Co | Tubular heat exchanger and method for its production |
| JPH04136690A (en) * | 1990-09-26 | 1992-05-11 | Showa Alum Corp | Heat exchanger |
| JPH10288476A (en) * | 1997-04-10 | 1998-10-27 | Sanden Corp | Heat-exchanger |
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| CN104081147A (en) * | 2012-02-02 | 2014-10-01 | 开利公司 | Multiple tube bank heat exchanger assembly and fabrication method |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2016085817A2 (en) | 2016-06-02 |
| US20170356700A1 (en) | 2017-12-14 |
| RU2693946C2 (en) | 2019-07-08 |
| RU2017121846A (en) | 2018-12-26 |
| EP3224565B1 (en) | 2023-12-27 |
| EP3224565A2 (en) | 2017-10-04 |
| WO2016085817A3 (en) | 2016-07-14 |
| RU2017121846A3 (en) | 2019-05-17 |
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