CN103270386A - Multiple Tube Bank Flattened Tube Finned Heat Exchanger - Google Patents
Multiple Tube Bank Flattened Tube Finned Heat Exchanger Download PDFInfo
- Publication number
- CN103270386A CN103270386A CN2011800618117A CN201180061811A CN103270386A CN 103270386 A CN103270386 A CN 103270386A CN 2011800618117 A CN2011800618117 A CN 2011800618117A CN 201180061811 A CN201180061811 A CN 201180061811A CN 103270386 A CN103270386 A CN 103270386A
- Authority
- CN
- China
- Prior art keywords
- tube bank
- tube
- heat exchanger
- heat
- under control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- 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
- F28D1/05358—Assemblies of conduits connected side by side or with individual headers, e.g. section type 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
- 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
- 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
-
- 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
- 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
- F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
- F28D2021/0063—Condensers
-
- 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
- F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
- F28D2021/0064—Vaporizers, e.g. 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
- F28F2215/00—Fins
- F28F2215/02—Arrangements of fins common to different heat exchange sections, the fins being in contact with different heat exchange media
Abstract
A multiple tube bank heat exchanger includes a first tube bank (100) including at least a first and a second flattened tube segments extending longitudinally in spaced parallel relationship and a second tube bank (200) including at least a first and a second flattened tube segments extending longitudinally in spaced parallel relationship. The second tube bank (200) is disposed behind the first tube bank (100) with a leading edge of the second tube bank spaced from a trailing edge of the first tube bank. A continuous folded plate fin extends between the first and second flattened tube segments of both of said first tube bank and said second tube bank.
Description
The cross reference of related application
Quote the U.S. Provisional Application sequence number 61/416 that the name of submitting on November 22nd, 2010 is called " multitubular bundles flattening pipe finned type heat exchanger (Multiple Tube Bank Flattened Tube Finned Heat Exchanger) ", 145 and the application require its priority and rights and interests, the full content of described application is incorporated this paper into way of reference.
Invention field
The present invention relates generally to heat exchanger, and more particularly, relate to flattening pipe and fin heat exchanger.
Background of invention
Heat exchanger is used as evaporimeter and condenser for a long time in heat supply, ventilation, air-conditioning and refrigeration (HVACR) are used.In history, these heat exchangers once were pipe and plate fin (RTPF) heat exchanger.Yet, flattening tube sheet fin heat exchanger in the use of industry in (comprising HVACR industry) more and more widely, this be because they compare with the RTPF heat exchanger of routine have compactedness, structural rigidity, than light weight and low cold-producing medium expense requirement.
Typical flattening tube sheet fin heat exchanger comprises first manifold, second manifold and single tube bank, and described single tube bank is formed by the flattening heat-exchange tube of a plurality of longitudinal extensions of settling with parallel relation at interval and extending between first manifold and second manifold.In addition, a plurality of plate fins are placed in each between the adjacent heat-exchange tube, with for increasing the fluid that flows on the outer surface that flows through the flattening pipe and along fin surface (in HVACR uses normally air) and heat transmission between the fluid of flattening pipe internal flow (in the HVACR application normally cold-producing medium).In the embodiment of normally used flattening pipe, it is called as multi-channel tube, small size tunnel pipe or microchannel tube in HVACR uses, and the inside of flattening pipe is subdivided into a plurality of parallel flow channels.For instance, U.S. Patent number 6,964,296 show a kind of flattening pipe flat fin heat exchanger in single tube bundle and two embodiments of two-tube bundle, it has horizontal tube layout and vertically extending flat fin.
A concern that is associated with use flattening pipe in pipe in HVACR uses is that condensate/water is bad from the discharge of flattening tube-surface.The delay of condensate/water may be a problem in the flattening pipe in pipe with the horizontal tube that has high fin density and compactron spacing especially.In this class formation, condensate/water tends to accumulate on the flat horizontal surface of the heat-exchange tube in the space between the intensive fin that piles up.Accumulate in corrosion and spot corrosion that condensate/water on the outer surface of heat exchanger tube serves as electrolyte and tends to the accelerating tube surface.Condensate/hydropexis on the horizontal surface of heat exchanger tube also can cause the pressure drop increase of air side and air stream to reduce, and equally also can cause undesirable condensate to blow out effect.Accumulate in the lip-deep any condensate/water of horizontal tube and also constitute the layer that heat transmission on the air side of heat-exchange tube increases resistance to heat.
Therefore, need a kind of flattening pipe finned type heat exchanger, its horizontal flat surface from the horizontally extending flattening heat-exchange tube of flattening is freely discharged condensate/water haply.A kind of flattening pipe finned type heat exchanger of same expectation, it freely discharges condensate/water haply, also realizes the hot property that strengthens simultaneously.
Summary of the invention
On the one hand, a kind of heat exchanger comprises: first tube bank, and described first tube bank comprises at least the first flattening area under control section and the second flattening area under control section, these sections are with parallel relation longitudinal extension at interval; Second tube bank, described second tube bank comprises at least the first flattening area under control section and the second flattening area under control section, these sections are with parallel relation longitudinal extension at interval, described second tube bank is placed in after described first tube bank, and the trailing edge of the leading edge of wherein said second tube bank and described first tube bank is spaced apart; And continuous folded fin plate, described fin plate extends between first tube bank and second both first flattening area under control sections of tube bank and the second flattening area under control section.Described continuous folded fin plate can comprise the venetian blind type plate, described venetian blind type plate has first venetian blind type part and the second venetian blind type part, described first venetian blind type part is extended between the first first flattening area under control section of restraining and the second flattening area under control section, and described second venetian blind type part is extended between the second first flattening area under control section of restraining and the second flattening area under control section.Described continuous folded sheet fin can further be included in the transition portion between first venetian blind type part and second venetian blind type part, and described transition portion is positioned between the trailing edge and second leading edge of restraining of first tube bank.The shutter of first venetian blind type part is with the forward direction angular orientation, and the shutter of second venetian blind type part is later on to angular orientation.Described transition portion can comprise condensate discharge recess.
On the one hand, provide a kind of heat exchanger, it is used for making cold-producing medium to become the mode of heat exchange relationship to pass through with the air stream of the air side of passing heat exchanger.Described heat exchanger comprises: first tube bank, and described first tube bank comprises a plurality of flattenings area under control section with parallel relation longitudinal extension at interval; With second tube bank, described second tube bank comprises a plurality of flattenings area under control section with parallel relation longitudinal extension at interval, described second tube bank is placed in the downstream about described first tube bank, wherein the trailing edge of the leading edge of second tube bank and first tube bank is spaced apart, wherein air stream at first is horizontally through the flattening area under control section of described first tube bank and then is horizontally through the described second flattening area under control section of restraining, and described cold-producing medium at first flows through the flattening heat-exchange tube section of described second tube bank and then flows through the described first flattening heat-exchange tube section of restraining.In one embodiment, the heat-exchange tube section of second tube bank is arranged in the mode that the heat-exchange tube section Cheng Shunlie with first tube bank arranges.In one embodiment, the heat-exchange tube section of second tube bank is arranged in the mode that the heat-exchange tube section with first tube bank becomes stagger arrangement to arrange.
On the one hand, provide a kind of parallel counterflow heat exchanger, it is used for making cold-producing medium to become the mode of heat exchange relationship to pass through with the air stream of the air side of passing heat exchanger.Described heat exchanger comprises at least the first tube bank and second tube bank, and each in the described tube bank has first pass, and described first pass comprises more than first flattening heat-exchange tube section with parallel relation longitudinal extension at interval; With second flow process, described second flow process comprises more than second flattening heat-exchange tube section with parallel relation longitudinal extension at interval.Air stream at first is horizontally through the flattening area under control section of described first tube bank, and secondly is horizontally through the flattening area under control section of described second tube bank.Cold-producing medium at first flows through the first pass of first tube bank, then flows through the first pass of second tube bank, then flows through second flow process of second tube bank, and then flows through second flow process of first tube bank.In one embodiment, be used as under the situation of evaporimeter fully adaptive, more than first heat-exchange tube section of the first pass of first tube bank defines the first flow of refrigerant zone jointly, and more than first heat-exchange tube section of the first pass of second tube bank defines the second flow of refrigerant zone jointly; More than second heat-exchange tube section of second flow process of second tube bank defines the 3rd flow of refrigerant zone jointly, and more than second heat-exchange tube section of second flow process of first tube bank defines the 4th flow of refrigerant zone jointly.Corresponding flow of refrigerant zone becomes big to the 4th flow of refrigerant zone more gradually from the first flow of refrigerant zone to three flow of refrigerant zones, the second flow of refrigerant zone to the.
The accompanying drawing summary
In order further to understand the disclosure, will be with reference to the following detailed description for the treatment of to read by reference to the accompanying drawings, in the accompanying drawings:
Fig. 1 is the graphical illustration of an exemplary of multitubular bundles flattening pipe finned type heat exchanger as disclosed herein;
Figure 1A is the fin and the side-looking sectional drawing of managing layout that the flattening pipe finned type heat exchanger of Fig. 1 is shown;
Fig. 2 is the cross-sectional plan view of a part of an exemplary of the multitubular bundles flattening pipe finned type heat exchanger that intercepts substantially of the line 2-2 along Fig. 1;
Fig. 3 is the side cross-sectional view of embodiment of the multitubular bundles flattening pipe finned type heat exchanger of Fig. 2;
Fig. 4 is the side cross-sectional view of an alternate embodiment of the multitubular bundles flattening pipe finned type heat exchanger of Fig. 3;
Fig. 5 is the single folding perspective view of the continuous folded fin plate of heat exchanger disclosed herein;
Fig. 6 is the cross-sectional plan view of passing the single folding fin of the folded fin plate shown in Fig. 5;
Fig. 7 is the schematic diagram of multi-pipe-bundle heat exchanger disclosed herein, and it illustrates an exemplary cross-counterflow refrigerant loop;
Fig. 8 is the schematic diagram of multi-pipe-bundle heat exchanger disclosed herein, and it illustrates another exemplary cross-counterflow refrigerant loop;
Fig. 9 is the schematic diagram of multi-pipe-bundle heat exchanger disclosed herein, and it illustrates another exemplary cross-counterflow refrigerant loop;
Figure 10 is the schematic diagram of multi-pipe-bundle heat exchanger disclosed herein, and it illustrates another exemplary cross-counterflow refrigerant loop;
Figure 11 is the schematic diagram of multi-pipe-bundle heat exchanger disclosed herein, and it illustrates another exemplary cross-counterflow refrigerant loop;
Figure 12 is the schematic diagram of multi-pipe-bundle heat exchanger disclosed herein, and it illustrates another exemplary cross-counterflow refrigerant loop;
Figure 13 is the schematic diagram of multi-pipe-bundle heat exchanger disclosed herein, and it illustrates a parallel adverse current refrigerant loop; And
Figure 14 is the side cross-sectional view of an exemplary of multitubular bundles flattening pipe finned type heat exchanger, and it illustrates first tube bank and second tube bank of arranging with the stagger arrangement heat-exchange tube.
Detailed Description Of The Invention
At first referring to the Fig. 1 among the figure and Fig. 2, describe an exemplary according to multi beam flattening pipe finned type heat exchanger 10 of the present invention.As describing at this, heat exchanger comprises first tube bank, 100 and at least the second tube bank 200, and described second tube bank is placed in first and restrains after 100.First tube bank, 100 and second tube bank each in 200 comprises first manifold 102 that extends along vertical axis, 202 and second manifold 104,204 that also extends along vertical axis.Should be appreciated that multi beam flattening pipe finned type heat exchanger 10 disclosed herein can comprise tube bank more than two.
In the heat-exchange tube section 106,206 each comprises the flattening heat-exchange tube, and described flattening heat-exchange tube has leading edge 108,208, trailing edge 110,210, upper planar surface 112,212 and lower flat surface 114,214.The inside of each in the heat-exchange tube section 106,206 can be separated into a plurality of parallel flow channels 120,220 by the inwall of longitudinal extension, and these parallel flow channels are restrained in first tube bank 100 and second and set up fluid between 200 the respective headers and be communicated with.Second tube bank 200 is placed in after first tube bank 100 about airflow direction, and wherein the leading edge 208 of second tube bank 200 is spaced apart with the relative narrow clearance G of about 2 millimeters (mm) to 4 millimeters (mm) (0.08 inch to 0.15 inch) with the trailing edge 110 of first tube bank 100.In the embodiment of describing, in the heat-exchange tube section 106,206 of first tube bank, 100 and second tube bank 200 each comprises a multi-channel tube respectively, described multi-channel tube has inner flow passage, described inner flow passage is separated into a plurality of discrete flow channels 120,220 by inwall, and these flow channel longitudinal extensions reach the length from the arrival end of pipe to the port of export of pipe of described pipe.Yet, should be appreciated that, tube bank 100,200 can comprise coiled pipe, heat-exchange tube section 106, the 206th wherein, and parallel linear area under control section, it is connected by return bend or hair clip bend pipe so that the coiled pipe that is connected at its associated end place between first manifold that is formed on tube bank and second manifold.
Flattening pipe finned type heat exchanger 10 disclosed herein further comprises a plurality of folded fin plates 20.Each folded fin plate 20 is formed by the single continuous fin material plate that closely folds with belt-like form, and the fin 22 of a plurality of tight spacings is provided thus, and these fins are orthogonal to flattening heat-exchange tube 106,206 substantially and extend.Typically, the fin density of the fin 22 of the tight spacing of each continuous folded fin plate 20 can be about 18 fins/inch to 25 fins/inch, but also can use higher or lower fin density.The trailing edge 110 and second that the degree of depth of each in the banded folded sheet 20 extends to the trailing edge 210 of second tube bank 200 and crosses over first tube bank 100 from the leading edge 108 of first tube bank 100 is restrained the clearance G between 200 the leading edge 208.In an embodiment of heat exchanger 10, manifold, heat-exchange tube and fin are all made by aluminum or aluminum alloy materials.
Now referring to Fig. 5 and Fig. 6, describe the single folding of continuous band-shaped folded fin plate 20 and show two fins 22.Each fin 22 has first 24, second portion 26 and third part 28.In the time of in being installed in heat exchanger 10, first 24 is placed in first tube bank 100, and third part 28 is placed in second tube bank 200, and the clearance G between the leading edge 208 of the trailing edge 110 of second portion 26 leaps first tube bank 100 and second tube bank 200.First 24 and second portion 28 can be provided with the shutter 30,32 that the material with fin plate 20 forms in a usual manner.In the embodiment of describing, the shutter 30 that forms in first 24 becomes forward angle with respect to the flow direction (being indicated by arrow) along fin 22 in Fig. 6, and the shutter 32 that forms in third part 28 becomes back azimuth with respect to the flow direction along fin 22.In the embodiment of describing, both become forward angle and back azimuth with desired shutter angle A respectively shutter in the shutter 30 in the first 24 of each fin 22 and the third part 28 32.Second portion 26 comprises and turns to shutter 34, and the described shutter that turns to provides transition between the shutter that becomes back azimuth 32 of the shutter 30 of the one-tenth forward angle of the first 24 of each fin 22 and third part 28.In the time of in being installed on heat exchanger 10, crossing over second portion 26 that first tube bank 100 and second restrains the clearance G between 200 and provide discharge path for the condensate/water on the upper planar surface 114,214 of the horizontal setting that accumulates in flattening heat-exchange tube section 106,206.
Depicted in figure 3 in the embodiment of heat exchanger 10, the heat-exchange tube section 106,206 that first tube bank, 100 and second tube bank 200 has an equal number, these sections between their manifolds separately with the same pipe spacing with parallel relation at interval vertically and horizontal-extending.In addition, heat-exchange tube section 206 is directly to aim to settle with heat-exchange tube section 106.In this layout, folded sheet fin 20 is placed between the alignment tube section group 106,206 of every pair of vicinity continuously.
Yet first tube bank, 100 and second tube bank 200 needn't have the heat-exchange tube section 106,206 of equal number.Or rather, can have the quantity different with the heat-exchange tube 206 in second tube bank 200 in the quantity of the heat-exchange tube 106 of first tube bank in 100.For instance, depicted in figure 4 in the embodiment of heat exchanger 10, being removed so that first tube bank 100 has the heat-exchange tube section 106 of the quantity of lacking than the quantity of the heat-exchange tube section 206 of second tube bank 200 every a heat-exchange tube 106 in first tube bank 100.In this particular, second tube bank 200 every an area under control section 206 direct aligning after first tube bank, 100 area under control section 106, and remaining area under control section 206 does not have arrangement respective tube section 106 at its upstream.
Should note, in area under control section 106 that first tube bank, 100 and second tube bank 200 has a varying number, 206 embodiment, a plurality of continuous folded fin plate 20 is extensible to pass through two tube banks, and wherein the quantity of fin plate 20 is determined to be and makes be mounted with continuous fin plate 20 between every pair of proximity thermal exchange area under control section with the heat-exchange tube section 106 of larger amt, tube bank of 206 continuously.Yet, perhaps, can remove some the fin parts in the tube bank of the heat-exchange tube section with lesser amt so that some but be not that all folded fin plates only extend to trailing edge from the leading edge of the tube bank of heat-exchange tube section with larger amt.
Equally can be variant between the pipe width of the heat-exchange tube section 106 in first tube bank 100 and the heat-exchange tube section 206 in second tube bank 200.In general, the heat-exchange tube section 106 of multi beam heat exchanger 10,206 width typically will be in the scope of 12mm to 32mm (about 0.5 inch to 1.5 inches).Because the flow channel 120 flattening heat-exchange tube section 106,206 in, 220 quantity typically change with the pipe width with being directly proportional respectively, thus respectively heat-exchange tube section 106,206 each in flow channel 120,220 quantity can difference and design at cold-producing medium thermophysical property (as density).
For instance, for the condenser heat exchanger in air-conditioning or refrigeration application, to have the area under control section 106 of comparing less width with the width of the heat-exchange tube section 206 of the second tube bank 206 upstream tube bank of cold-producing medium stream (namely about) about the heat-exchange tube of the downstream tube bank of cold-producing medium stream (it will be first tube bank 100) in Fig. 1 and embodiment depicted in figure 3, to adapt to condensation of refrigerant technology and in the passage of the intrafascicular heat-exchange tube section of downstream tube, to keep desired flow of refrigerant speed, in order to obtain the appropriate balance between heat transmission and Pressure Drop Characteristics.
With respect to the quantity at the intrafascicular heat-exchange tube section of the upstream tube that flows about cold-producing medium, minimizing is in the quantity about the intrafascicular heat-exchange tube section of the downstream tube of cold-producing medium stream, no matter whether in conjunction with the width that shortens at the intrafascicular heat-exchange tube section of downstream tube, also be effective adapting to condensation of refrigerant technology and maintaining aspect institute's flow of refrigerant speed of wanting in the flow channel of the intrafascicular heat-exchange tube section of downstream tube, thereby obtain the appropriate balance between heat transmission and Pressure Drop Characteristics.In addition, can reduce to adapt to condensed refrigerant stream by the cross section flow region that reduces a plurality of flow channels or the quantity that reduces flow channel by the cross section flow region about the heat-exchange tube section of the downstream tube bank of cold-producing medium stream, keep simultaneously with about the identical outside geometric properties of the outside geometric properties of the upstream tube bank of cold-producing medium stream.
These concepts can be applied to evaporator heat exchanger in air-conditioning or refrigeration application by the reverse mode.For instance, for evaporator heat exchanger, can have area under control section with the low width of comparing about the width of the heat-exchange tube section of the downstream tube bank of cold-producing medium stream about the heat-exchange tube of the upstream tube bank of cold-producing medium stream.
A plurality of tube banks in conjunction with the heat-exchange tube section with different in width, the venetian blind type fin 22 of continuous folded fin plate 20 can be asymmetric, and wherein the size of first 24 and third part 28 is differently set to mate the respective tube width of first tube bank, 100 and second tube bank 200.If heat-exchange tube section 106,206 has the pipe of equating width, the first fin part 24 of fin 22 and the 3rd fin part 28 have the centre of second portion 26 (that is, turning to the shutter part) between first 24 and third part 28 of equal length and fin 22 so.Yet for the heat exchanger configuration of the tube bank with different pipe width, second portion 26 (that is, turning to the shutter part) delocalization is in the central authorities of fin 22, but is arranged in to offset from center fin between the first 24 of fin and third part 28.
In any case, second portion 26 (namely, turning to the shutter part) trailing edge and second that should aim to cross over first tube bank 100 again restrains the clearance G between 200 the leading edge, as shown in Fig. 3 and Fig. 4, because the clearance G between shutter part 26 and the tube bank that turns to of venetian blind type fin 22 is aimed at the improved discharge of condensate/water from the surface of flattening heat-exchange tube section is provided.Turning to the shutter place to exist the design of recess will make needs use asymmetric shutter bundle.
Now again referring to Fig. 1, multitubular bundles flattening pipe finned type heat exchanger 10 will be described to be configured to the condenser heat exchanger in the refrigerant vapor compression system of air-conditioning unit, transport refrigeration unit or commercial refrigeration unit.In this type of is used, from the refrigerant vapour of the compressor (not shown) of refrigerant vapor compression system (not shown) with the mode that describes in further detail hereinafter with become heat exchange relationship to pass manifold and the heat-exchange tube section of tube bank 100,200 at the cooling medium (the most normally surrounding air) by the air side of the indicated direction upper reaches over-heat-exchanger 10 of the arrow that is labeled as " A ", described cooling medium is crossed heat-exchange tube section 106,206 outer surface and the surface of folded fin plate 20.
Multitubular bundles flattening pipe finned type heat exchanger 10 depicted in figure 1 has the cross-counterflow loop and arranges.Air stream at first is horizontally through the upper horizontal surface 112 of heat-exchange tube section 106 of first tube bank and lower horizontal surface 114 and then is horizontally through upper horizontal surface 212 and the lower horizontal surface 214 of the heat-exchange tube section 206 of second tube bank 200.Cold-producing medium passes through to become to intersect the mode of counter-flow arrangement with air stream, because cold-producing medium stream at first passes second tube bank 200 and then passes first tube bank 100.In described process, the cold-producing medium refusal heat that passes heat-exchange tube 106,206 flow channel enters in the air stream of the air side of passing heat exchanger 10.Have the multitubular bundles flattening pipe finned type heat exchanger 10 arranged in the cross-counterflow loop and cross flow one or intersect and flow back to the road and arrange to compare and produce superior performance.
More particularly, depicted in figure 1 in the embodiment, pass first manifold 202 that enters second tube bank 200 and be distributed in the middle of the heat-exchange tube section 206 to flow in second manifold 204 of second tube bank 200 by these sections from refrigerant loop (not shown) by the indicated cold-producing medium stream of label " R ".The cold-producing medium of assembling in second tube bank, 200 second manifold 204 passes in the bottom part 116 of second manifold 104 that enters first tube bank 100 subsequently and is distributed in the middle of the first of heat-exchange tube section 106 to flow into by described part and restrains in 100 first manifold 102.Cold-producing medium passes the second portion that enters heat-exchange tube section 106 and flows into by described second portion in the top 118 of second manifold 104 of first tube bank 100 and lead back to thus in the refrigerant loop of refrigerant vapor compression system (not shown) from first manifold 102.Therefore, the refrigerant loop of the embodiment of multi beam heat exchanger depicted in figure 1 is the cross-counterflow refrigerant loop of a single process-double-current journey.
Referring now to Fig. 7, to Figure 11, schematically shows various other exemplary that the acceptable refrigerant loop of the two-tube bundle heat exchanger 10 of cross-counterflow is arranged.In each figure of Figure 10, the air stream that passes the air side of heat exchanger is by the indicated cross-counterflow of arrow " A " and at first by first tube bank 100 and then by second tube bank 200, as before discussing about Fig. 1 at Fig. 7.The cold-producing medium stream indicated by arrow " R " becomes the form of whole cross-counterflow at first by second tube bank 200 and then by first tube bank 100 with the air with the air side of passing heat exchanger 10.In the embodiment, cold-producing medium flows back to the cross-counterflow refrigerant loop that the road comprises a single process-single process depicted in figure 7.In the embodiment, cold-producing medium flows back to the cross-counterflow refrigerant loop that the road comprises a double-current journey-double-current journey depicted in figure 8.Depicted in figure 9 in the embodiment, cold-producing medium flows back to a single process-double-current journey version of the cross-counterflow refrigerant loop of single process-double-current journey that the road comprises Fig. 1.In the embodiment, cold-producing medium flows back to the cross-counterflow refrigerant loop that the road comprises double-current journey-three flow process depicted in figure 10.
Referring now to Figure 11 and Figure 12,, schematically show the exemplary that the acceptable refrigerant loop of three tube bundle heat exchangers 10 of cross-counterflow is arranged.In each figure of Figure 12, the air stream that passes the air side of heat exchanger is by the indicated cross-counterflow of arrow " A " and at first passes first tube bank 100, then passes second tube bank 200 and passes the 3rd tube bank 300 at last at Figure 11.The cold-producing medium stream indicated by arrow " R " becomes the form of whole adverse current at first to pass the 3rd tube bank 300 with the air with the air side of passing heat exchanger 10, then passes second tube bank 200 and passes first tube bank 100 at last.In the embodiment, cold-producing medium flows back to the cross-counterflow refrigerant loop that the road comprises a single process-single process-single process depicted in figure 11.In the embodiment, cold-producing medium flows back to the cross-counterflow refrigerant loop that the road comprises a single process-double-current journey-three flow process depicted in figure 12.
Referring now to Figure 13,, describe multitubular bundles flattening pipe in pipe 400, it has three tube banks 100,200,300 that are parallel counter-flow arrangement.Depicted in figure 13 in the embodiment, at first pass first tube bank 100 by the air stream of the indicated air side of passing through heat exchanger of arrow " A ", then pass second tube bank 200, and pass the 3rd tube bank 300 at last.In the tube bank 100,200,300 each comprises a double-current journey tube bank, has a bottom flow process 130,230,330 respectively, and has a top flow process 140,240,340 respectively.Be parallel to the air stream that passes heat exchanger 400 at first substantially and follow reverse in the air stream that passes heat exchanger 400 substantially by the indicated cold-producing medium stream of arrow " R ".Cold-producing medium at first passes the bottom flow process 130 of first tube bank 100, then pass the bottom flow process 230 of second tube bank 200, then pass the bottom flow process 330 of the 3rd tube bank 300, then pass the top flow process 340 of the 3rd tube bank 300, then pass second tube bank, 200 top flow process 240, and pass the top flow process 140 of first tube bank 100 at last and get back in the refrigerant loop (not shown).Depicted in figure 13 in the embodiment of heat exchanger 400, the quantity of heat-exchange tube section little by little changes in the middle of flow process 130,230,330,340,240,140, wherein the heat-exchange tube section of minimum number is in first tube bank, 100 bottom flow process 130, then increases gradually from flow process 230,330,340, the 240 top flow processs 140 to first tube bank 100 of the heat-exchange tube with maximum quantity.The evaporimeter that multi beam flattening pipe in pipe 400 is especially suitable for use as in the refrigerant vapor compression system, because the flow of refrigerant zone that provides when flowing through three tube bank each flow processs of 100,200,300 along with cold-producing medium in the process of the flow process of cumulative pipe quantity as herein described increases gradually, reason is that this layout adapts to the density of cold-producing medium along with cold-producing medium passes the variation that evaporimeter produces.Should be appreciated that under the situation that condensation of refrigerant technology should be carried out in heat exchanger tube inside, the pipe quantity in each section can reduce gradually.
By the loop of various abundant optimizations, as illustrated in the refrigerant loop of being discussed by this paper, heat transmitting can improve, and refrigerant side pressure drop or power of fan do not have tangible infringement.Single bundle flattening pipe in pipe of the coil volume of the performance of the enhancing of multitubular bundles flattening pipe finned type heat exchanger 10 permission heat exchanger and front face area and routine is compared and is reduced up to 25% as disclosed herein.
Referring now to Figure 14,, describe an exemplary of multi beam flattening pipe folded fin platelet heat exchangers 50, it has first tube bank, 510 and second tube bank 520, described first tube bank has a plurality of multi-channel heat exchange tubes sections 512, and described second tube bank has a plurality of multi-channel tube 522.The heat-exchange tube section 512 of first tube bank 510 relation with parallel interval between first manifold (not shown) and second manifold (not shown) is extended, as restraining 100 modes of being discussed with previous about first of heat exchanger 10.Similarly, the heat-exchange tube section 522 of second tube bank 520 relation with parallel interval between first manifold (not shown) and second manifold (not shown) is extended, as restraining 200 modes of being discussed with previous about second of heat exchanger 10.Yet, in heat exchanger 50, second tube bank 520 with at interval relation arranges with narrow relatively clearance G that in the downstream about the air stream of the air side of passing first tube bank, 510 heat exchanger 50 wherein heat-exchange tube section 522 is to settle with the form that 512 one-tenths stagger arrangement of heat-exchange tube section of first tube bank 510 concern.
In addition, more than first folded fin plate 530 is arranged in first tube bank 510, one of them folded fin plate 530 is installed between every pair of adjacent heat-exchange tube section 510 and with these sections and becomes heat transfer relation, and more than second folded fin plate 540 is arranged in second tube bank 520, and one of them folded fin plate 540 is installed between every pair of adjacent heat-exchange tube section 520 and with these sections and becomes heat transfer relation.In the folded fin plate 530,540 each comprises a continuous band-shaped folded sheet, and it defines a plurality of fins 532,542 respectively, and these fins are orthogonal to heat-exchange tube section 512,522 and extend respectively substantially.Each comprised venetian blind type fin in the described fin.Each folded fin plate 530 extends to trailing edge from the leading edge of the heat-exchange tube section 512 of first tube bank 510, but does not extend in second tube bank 520.Each folded fin plate 540 extends to trailing edge from the leading edge of the heat-exchange tube section 522 of first tube bank 520, but does not extend in first tube bank 510.Term as used herein is the purpose unrestricted for description.It is restrictive that ad hoc structure disclosed herein and function detail should not be construed as, but adopt basis of the present invention as just instruction those skilled in the art.Those of skill in the art also will appreciate that the described element of alternative reference exemplary disclosed herein and do not break away from the equivalent of the scope of the invention.
Though the present invention with reference to as described in the exemplary as shown in the figure carried out concrete displaying and description, those skilled in the art will recognize that, can under the situation that does not break away from the spirit and scope of the present invention, make various modifications.Should also be clear that heat exchanger disclosed herein can be combined in that employed refrigerant vapor compression system uses in air-conditioning, heat pump and the refrigeration application.Therefore, wish that the disclosure is not limited to disclosed one or more particular, but the disclosure will comprise falling all embodiments within the scope of the appended claims.
Claims (18)
1. heat exchanger, it comprises:
First tube bank, it comprises at least the first flattening area under control section and the second flattening area under control section, described section is with parallel relation longitudinal extension at interval;
Second tube bank, it comprises at least the first flattening area under control section and the second flattening area under control section, described section is with parallel relation longitudinal extension at interval, and described second tube bank is placed in after described first tube bank, and the trailing edge of the leading edge of wherein said second tube bank and described first tube bank is spaced apart; And
The folded sheet fin extends between described first tube bank and described second both described first flattening area under control sections of tube bank and the described second flattening area under control section continuously.
2. heat exchanger as claimed in claim 1, wherein said continuous folded sheet fin comprises the venetian blind type plate, and described venetian blind type plate has in first venetian blind type part of extending between the described first flattening area under control section and the described second flattening area under control section of described first tube bank and the second venetian blind type part of extending between the described second described first flattening area under control section of restraining and the described second flattening area under control section.
3. heat exchanger as claimed in claim 2, wherein said continuous folded sheet fin further is included in the transition portion between described first venetian blind type part and described second venetian blind type part, and described transition portion is positioned between the trailing edge and described second leading edge of restraining of described first tube bank.
4. heat exchanger as claimed in claim 3, wherein said transition portion comprises the condensate tap.
5. heat exchanger as claimed in claim 3, wherein said first venetian blind type part partly is symmetrical with described second venetian blind type.
6. heat exchanger as claimed in claim 3, wherein said first venetian blind type part partly is asymmetric with described second venetian blind type.
7. heat exchanger as claimed in claim 2, the shutter of wherein said first venetian blind type part with the shutter of forward direction angular orientation and described second venetian blind type part after to angular orientation.
8. heat exchanger as claimed in claim 5, wherein said continuous folded sheet fin further is included in the transition portion between described first venetian blind type part and described second venetian blind type part, and described transition portion is positioned between the trailing edge and described second leading edge of restraining of described first tube bank.
9. heat exchanger as claimed in claim 8, wherein said transition portion comprises the condensate tap.
10. heat exchanger as claimed in claim 1, the tube bank that comprises the flattening area under control section with equal number is restrained in wherein said first tube bank and described second.
11. heat exchanger as claimed in claim 1, one in wherein said first tube bank and described second tube bank comprise the tube bank of comparing the flattening area under control section with lesser amt with described first tube bank and another person's during described second restrains tube bank.
12. heat exchanger as claimed in claim 1, the described flattening area under control section of wherein said first tube bank have the described flattening area under control section of the first pipe width and described second tube bank and have the second pipe width that is different from the described first pipe width.
13. heat exchanger as claimed in claim 1, each flattening area under control section of wherein said first tube bank comprises the multi-channel tube section, described multi-channel tube section has more than first parallel flow channels, and each flattening area under control section of described second tube bank comprises the multi-channel tube section, described multi-channel tube section has more than second parallel flow channels, and the quantity of described more than second parallel flow channels is different from the quantity of described more than first parallel flow channels.
14. a heat exchanger, it is used for making cold-producing medium to become the mode of heat exchange relationship to pass through with the air stream of the air side of passing described heat exchanger, and described heat exchanger comprises:
First tube bank, it comprises a plurality of flattenings area under control section with parallel relation longitudinal extension at interval; And
Second tube bank, it comprises a plurality of flattenings area under control section with parallel relation longitudinal extension at interval, and described second tube bank is placed in the downstream about described first tube bank, and the trailing edge of the leading edge of wherein said second tube bank and described first tube bank is spaced apart;
Wherein said air stream at first is horizontally through the described flattening area under control section of described first tube bank and then is horizontally through the described flattening area under control section of described second tube bank, and described cold-producing medium at first flows through the described flattening heat-exchange tube section of described second tube bank and then flows through the described first described flattening heat-exchange tube section of restraining.
15. heat exchanger as claimed in claim 14, the described heat-exchange tube section of wherein said second tube bank is arranged in the mode that the described heat-exchange tube section Cheng Shunlie with described first tube bank arranges.
16. heat exchanger as claimed in claim 14, the described heat-exchange tube section of wherein said second tube bank is arranged in the mode that the described heat-exchange tube section with described first tube bank becomes stagger arrangement to arrange.
17. a heat exchanger, it is used for making cold-producing medium to become the mode of heat exchange relationship to pass through with the air stream of the air side of passing described heat exchanger, and described heat exchanger comprises:
At least the first tube bank and second tube bank, each in the described tube bank has first pass, and described first pass comprises more than first flattening heat-exchange tube section with parallel relation longitudinal extension at interval; And second flow process, described second flow process comprises more than second flattening heat-exchange tube section with parallel relation longitudinal extension at interval;
Wherein said air stream at first is horizontally through the described flattening area under control section of described first tube bank and secondly is horizontally through the described flattening area under control section of described second tube bank, and described cold-producing medium at first flows through the described first pass of described first tube bank, then flow through the described first pass of described second tube bank, then flow through described second flow process of described second tube bank, and then flow through described second flow process of described first tube bank.
18. heat exchanger as claimed in claim 17, described more than first the heat-exchange tube section of the described first pass of wherein said first tube bank defines the first flow of refrigerant zone jointly, and described more than first the heat-exchange tube section of the described first pass of described second tube bank defines the second flow of refrigerant zone jointly; Described more than second the heat-exchange tube section of described second flow process of described second tube bank defines the 3rd flow of refrigerant zone jointly, and described more than second the heat-exchange tube section of described second flow process of described first tube bank defines the 4th flow of refrigerant zone jointly, and corresponding flow of refrigerant zone again to described four flow of refrigerant zone gradually becomes big to the described second flow of refrigerant zone to described the 3rd flow of refrigerant zone from the described first flow of refrigerant zone.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US41614510P | 2010-11-22 | 2010-11-22 | |
| US61/416,145 | 2010-11-22 | ||
| PCT/US2011/060506 WO2012071196A2 (en) | 2010-11-22 | 2011-11-14 | Multiple tube bank flattened tube finned heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103270386A true CN103270386A (en) | 2013-08-28 |
Family
ID=44999975
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011800618117A Pending CN103270386A (en) | 2010-11-22 | 2011-11-14 | Multiple Tube Bank Flattened Tube Finned Heat Exchanger |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20130240186A1 (en) |
| EP (1) | EP2643650A2 (en) |
| CN (1) | CN103270386A (en) |
| WO (1) | WO2012071196A2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106796091A (en) * | 2014-10-07 | 2017-05-31 | 三菱电机株式会社 | Heat exchanger and conditioner |
| CN106796092A (en) * | 2014-10-07 | 2017-05-31 | 三菱电机株式会社 | Heat exchanger and air-conditioning device |
| CN107003073A (en) * | 2014-11-26 | 2017-08-01 | 开利公司 | The micro channel heat exchanger of resistance to frost |
| WO2017197908A1 (en) * | 2016-05-16 | 2017-11-23 | 丹佛斯微通道换热器（嘉兴）有限公司 | Heat exchanger and heat exchange module |
| CN107702382A (en) * | 2017-05-24 | 2018-02-16 | 杭州三花家电热管理系统有限公司 | micro-channel evaporator |
| CN111322795A (en) * | 2018-12-14 | 2020-06-23 | 丹佛斯有限公司 | Heat exchanger and air conditioning system |
Families Citing this family (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104995471A (en) | 2013-02-13 | 2015-10-21 | 开利公司 | Multiple bank flattened tube heat exchanger |
| EP2972037B1 (en) * | 2013-03-15 | 2018-11-21 | Carrier Corporation | Heat exchanger for air-cooled chiller |
| US10830542B2 (en) | 2013-05-15 | 2020-11-10 | Carrier Corporation | Method for manufacturing a multiple manifold assembly having internal communication ports |
| EP3014011B1 (en) * | 2013-06-24 | 2018-08-08 | Electrolux Appliances Aktiebolag | Heat pump laundry dryer |
| WO2015070901A1 (en) * | 2013-11-13 | 2015-05-21 | Electrolux Appliances Aktiebolag | Heat pump laundry dryer |
| ITBO20130632A1 (en) * | 2013-11-20 | 2015-05-21 | Gas Point S R L | PLATE HEAT EXCHANGER, IN PARTICULAR FOR CONDENSING BOILERS |
| US9561819B2 (en) | 2013-12-19 | 2017-02-07 | Cnh Industrial America Llc | System and method for actively determining a steering stop angle for a work vehicle |
| CN203704716U (en) * | 2013-12-31 | 2014-07-09 | 力博特公司 | Microchannel heat exchanger capable of improving dirt-resisting and anti-blocking capabilities |
| US10252611B2 (en) * | 2015-01-22 | 2019-04-09 | Ford Global Technologies, Llc | Active seal arrangement for use with vehicle condensers |
| EP3504948B1 (en) * | 2016-08-26 | 2022-11-09 | Inertech IP LLC | Cooling systems and methods using single-phase fluid and a flat tube heat exchanger with counter-flow circuiting |
| CN206420193U (en) | 2017-01-20 | 2017-08-18 | 丹佛斯微通道换热器（嘉兴）有限公司 | Heat exchanger assembly |
| US11022382B2 (en) * | 2018-03-08 | 2021-06-01 | Johnson Controls Technology Company | System and method for heat exchanger of an HVAC and R system |
| WO2019183503A2 (en) * | 2018-03-22 | 2019-09-26 | Nelumbo Inc. | Heat exchangers and methods of manufacture thereof |
| US10976084B2 (en) * | 2018-09-05 | 2021-04-13 | Audi Ag | Evaporator in a refrigerant circuit a |
| US10895410B2 (en) * | 2018-09-05 | 2021-01-19 | Audi Ag | Evaporator in a refrigerant circuit B |
| DE102018218687A1 (en) | 2018-10-31 | 2020-04-30 | Mahle International Gmbh | Heat exchanger for an air conditioning system |
| US11236951B2 (en) | 2018-12-06 | 2022-02-01 | Johnson Controls Technology Company | Heat exchanger fin surface enhancement |
| CN112747502A (en) * | 2019-10-29 | 2021-05-04 | 浙江盾安热工科技有限公司 | Heat exchanger |
| WO2022215193A1 (en) * | 2021-04-07 | 2022-10-13 | 三菱電機株式会社 | Refrigeration cycle device |
| EP4134612A1 (en) * | 2021-08-10 | 2023-02-15 | Valeo Vymeniky Tepla S.r.o. | A heat exchanger |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5086835A (en) * | 1989-04-24 | 1992-02-11 | Sanden Corporation | Heat exchanger |
| CN1410738A (en) * | 2001-09-29 | 2003-04-16 | 汉拏空调株式会社 | Heat exchanger |
| US20040021683A1 (en) * | 1999-02-01 | 2004-02-05 | Qian Huang | Synthetic audiovisual description scheme, method and system for MPEG-7 |
| CN1820177A (en) * | 2003-07-08 | 2006-08-16 | 昭和电工株式会社 | Evaporator |
| US20070051502A1 (en) * | 2004-05-19 | 2007-03-08 | Showa Denko K.K. | Heat exchanger fin, heat exchanger, condensers, and evaporators |
| US20070084589A1 (en) * | 2005-10-18 | 2007-04-19 | Denso Corporation | Evaporator |
| CN101315231A (en) * | 2007-06-01 | 2008-12-03 | 株式会社电装 | Heat exchanger core, heat exchanger, and evaporator of refrigeration cycle apparatus |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3161234A (en) * | 1962-10-16 | 1964-12-15 | United Aircraft Corp | Multipass evaporator |
| US4712612A (en) * | 1984-10-12 | 1987-12-15 | Showa Aluminum Kabushiki Kaisha | Horizontal stack type evaporator |
| US5289874A (en) * | 1993-06-28 | 1994-03-01 | General Motors Corporation | Heat exchanger with laterally displaced louvered fin sections |
| US6070428A (en) * | 1997-05-30 | 2000-06-06 | Showa Aluminum Corporation | Stack type evaporator |
| JP4117429B2 (en) * | 1999-02-01 | 2008-07-16 | 株式会社デンソー | Heat exchanger fins |
| JP4379967B2 (en) * | 1999-03-30 | 2009-12-09 | 株式会社デンソー | Double heat exchanger |
| US6964296B2 (en) | 2001-02-07 | 2005-11-15 | Modine Manufacturing Company | Heat exchanger |
| US7337832B2 (en) * | 2003-04-30 | 2008-03-04 | Valeo, Inc. | Heat exchanger |
| DE102004018317A1 (en) * | 2004-04-13 | 2005-11-03 | Behr Gmbh & Co. Kg | Heat exchanger for motor vehicles |
| US20070251681A1 (en) * | 2004-10-13 | 2007-11-01 | Naohisa Higashiyama | Evaporator |
| FR2914407B1 (en) * | 2007-03-30 | 2009-12-11 | Valeo Systemes Thermiques | IMPROVED EVAPORATOR FOR A COOLING SYSTEM OF A MOTOR VEHICLE |
| DE202010000951U1 (en) * | 2010-01-22 | 2010-04-22 | Behr Gmbh & Co. Kg | Heat exchangers, in particular gas coolers for air conditioning systems in motor vehicles |
-
2011
- 2011-11-14 EP EP11785273.1A patent/EP2643650A2/en not_active Ceased
- 2011-11-14 CN CN2011800618117A patent/CN103270386A/en active Pending
- 2011-11-14 US US13/988,568 patent/US20130240186A1/en not_active Abandoned
- 2011-11-14 WO PCT/US2011/060506 patent/WO2012071196A2/en active Application Filing
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5086835A (en) * | 1989-04-24 | 1992-02-11 | Sanden Corporation | Heat exchanger |
| US20040021683A1 (en) * | 1999-02-01 | 2004-02-05 | Qian Huang | Synthetic audiovisual description scheme, method and system for MPEG-7 |
| CN1410738A (en) * | 2001-09-29 | 2003-04-16 | 汉拏空调株式会社 | Heat exchanger |
| CN1820177A (en) * | 2003-07-08 | 2006-08-16 | 昭和电工株式会社 | Evaporator |
| US20070051502A1 (en) * | 2004-05-19 | 2007-03-08 | Showa Denko K.K. | Heat exchanger fin, heat exchanger, condensers, and evaporators |
| US20070084589A1 (en) * | 2005-10-18 | 2007-04-19 | Denso Corporation | Evaporator |
| CN101315231A (en) * | 2007-06-01 | 2008-12-03 | 株式会社电装 | Heat exchanger core, heat exchanger, and evaporator of refrigeration cycle apparatus |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106796091B (en) * | 2014-10-07 | 2019-05-10 | 三菱电机株式会社 | Heat exchanger and conditioner |
| CN106796092A (en) * | 2014-10-07 | 2017-05-31 | 三菱电机株式会社 | Heat exchanger and air-conditioning device |
| CN106796091A (en) * | 2014-10-07 | 2017-05-31 | 三菱电机株式会社 | Heat exchanger and conditioner |
| US10605502B2 (en) | 2014-10-07 | 2020-03-31 | Mitsubishi Electric Corporation | Heat exchanger and air-conditioning apparatus |
| CN106796092B (en) * | 2014-10-07 | 2019-06-21 | 三菱电机株式会社 | Heat exchanger and air-conditioning device |
| US10082322B2 (en) | 2014-10-07 | 2018-09-25 | Mitsubishi Electric Corporation | Heat exchanger and air-conditioning apparatus |
| CN107003073A (en) * | 2014-11-26 | 2017-08-01 | 开利公司 | The micro channel heat exchanger of resistance to frost |
| WO2017197908A1 (en) * | 2016-05-16 | 2017-11-23 | 丹佛斯微通道换热器（嘉兴）有限公司 | Heat exchanger and heat exchange module |
| EP3460359A4 (en) * | 2016-05-16 | 2020-01-08 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co. Ltd. | Heat exchanger and heat exchange module |
| CN107388637A (en) * | 2016-05-16 | 2017-11-24 | 丹佛斯微通道换热器（嘉兴）有限公司 | Heat exchanger and heat exchange module |
| US10801783B2 (en) | 2016-05-16 | 2020-10-13 | Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. | Heat exchanger and heat exchange module |
| CN107388637B (en) * | 2016-05-16 | 2023-04-28 | 丹佛斯微通道换热器（嘉兴）有限公司 | Heat exchanger and heat exchange module |
| CN107702382A (en) * | 2017-05-24 | 2018-02-16 | 杭州三花家电热管理系统有限公司 | micro-channel evaporator |
| CN111322795A (en) * | 2018-12-14 | 2020-06-23 | 丹佛斯有限公司 | Heat exchanger and air conditioning system |
| US11549762B2 (en) | 2018-12-14 | 2023-01-10 | Danfoss A/S | Heat exchanger and air-conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2012071196A2 (en) | 2012-05-31 |
| WO2012071196A3 (en) | 2013-02-28 |
| US20130240186A1 (en) | 2013-09-19 |
| EP2643650A2 (en) | 2013-10-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103270386A (en) | Multiple Tube Bank Flattened Tube Finned Heat Exchanger | |
| US20200348088A1 (en) | Flattened tube finned heat exchanger and fabrication method | |
| US10508862B2 (en) | Heat exchanger for air-cooled chiller | |
| US9631841B2 (en) | Refrigerant evaporator | |
| EP2369285B1 (en) | Heat exchanger | |
| CN103477177B (en) | Heat exchanger | |
| US20110240276A1 (en) | Heat exchanger having an inlet distributor and outlet collector | |
| US20150345843A1 (en) | Refrigerant distributor of micro-channel heat exchanger | |
| CN101419002B (en) | Parallel flow heat exchanger and use | |
| US20170343288A1 (en) | Multi-pass and multi-slab folded microchannel heat exchanger | |
| KR101748242B1 (en) | Refrigerant evaporator | |
| CN211855020U (en) | Heat exchange tube and heat exchanger with same | |
| JP6131705B2 (en) | Refrigerant evaporator | |
| US10386124B2 (en) | Dual pass opposed (reverse) flow cooling coil with improved performance | |
| JP6785137B2 (en) | Evaporator | |
| EP3137836A1 (en) | Improved heat exchanger | |
| JP2018087646A5 (en) | ||
| US20220252349A1 (en) | Heat exchanger | |
| JP2003222436A (en) | Heat exchanger for heat pump type air conditioner | |
| CN112964111B (en) | Heat exchange tube and heat exchanger with same | |
| CN101226022A (en) | Micro space parallel flow heat exchanger | |
| CN212902102U (en) | Heat exchanger and refrigerating and heating system with same | |
| JP2003294338A (en) | Heat exchanger | |
| JP6486212B2 (en) | Evaporator and vehicle air conditioner using the same | |
| JP6432275B2 (en) | Refrigerant evaporator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20130828 |