CN101142452A - Flat tube single snake-like co2 heat exchanger - Google Patents
Flat tube single snake-like co2 heat exchanger Download PDFInfo
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- CN101142452A CN101142452A CNA200580049152XA CN200580049152A CN101142452A CN 101142452 A CN101142452 A CN 101142452A CN A200580049152X A CNA200580049152X A CN A200580049152XA CN 200580049152 A CN200580049152 A CN 200580049152A CN 101142452 A CN101142452 A CN 101142452A
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- fin
- tube heat
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- 239000003507 refrigerant Substances 0.000 claims abstract description 18
- 238000005057 refrigeration Methods 0.000 claims abstract description 13
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 6
- 239000012530 fluid Substances 0.000 claims description 41
- 230000006835 compression Effects 0.000 claims description 12
- 238000007906 compression Methods 0.000 claims description 12
- 235000013361 beverage Nutrition 0.000 claims description 5
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- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 2
- 239000004411 aluminium Substances 0.000 claims description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 2
- 229910052782 aluminium Inorganic materials 0.000 claims description 2
- 230000000712 assembly Effects 0.000 claims description 2
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- PZZOEXPDTYIBPI-UHFFFAOYSA-N 2-[[2-(4-hydroxyphenyl)ethylamino]methyl]-3,4-dihydro-2H-naphthalen-1-one Chemical compound C1=CC(O)=CC=C1CCNCC1C(=O)C2=CC=CC=C2CC1 PZZOEXPDTYIBPI-UHFFFAOYSA-N 0.000 description 5
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- 238000010521 absorption reaction Methods 0.000 description 2
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- WYTGDNHDOZPMIW-RCBQFDQVSA-N alstonine Natural products C1=CC2=C3C=CC=CC3=NC2=C2N1C[C@H]1[C@H](C)OC=C(C(=O)OC)[C@H]1C2 WYTGDNHDOZPMIW-RCBQFDQVSA-N 0.000 description 1
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
- F28D1/0478—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
- F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
- F25D19/02—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors plug-in type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/065—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air return
- F25D2317/0651—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air return through the bottom
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/066—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air supply
- F25D2317/0661—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air supply from the bottom
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2323/00—General constructional features not provided for in other groups of this subclass
- F25D2323/002—Details for cooling refrigerating machinery
- F25D2323/0026—Details for cooling refrigerating machinery characterised by the incoming air flow
- F25D2323/00264—Details for cooling refrigerating machinery characterised by the incoming air flow through the front bottom part
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2323/00—General constructional features not provided for in other groups of this subclass
- F25D2323/002—Details for cooling refrigerating machinery
- F25D2323/0027—Details for cooling refrigerating machinery characterised by the out-flowing air
- F25D2323/00271—Details for cooling refrigerating machinery characterised by the out-flowing air from the back bottom
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D2021/0073—Gas coolers
Abstract
A refrigeration system includes 0 compressor for driving 0 refrigerant along flow path in at least a first mode of system ; a first heat exchanger along the flow path downstream of the compressor in the first mode; a second heat exchanger along the flow path upstream the compressor in the first mode; and a pressure regulator or expansion device in the flow path downstream of the first heat exchanger and upstream of the second heat exchanger in the first mode, wherein at least one of the first heat exchanger and the second heat exchanger comprises a flat tube heat exchanger.
Description
Technical field
[0002] the present invention relates to the design of heat exchanger tube, and more particularly, relate to a kind of and/or with the design of striding the heat exchanger that critical steam compression system is connected, this heat exchanger applications is in narrow field, the space of heat exchanger.
Background technology
[0003] heat exchange efficiency is relevant with heat exchanger, for example the heat exchanger that uses in difference refrigeration and other air-treatments application.Have different heat exchanger types now, have the pipeline of fin and other likes.And the requirement of heat exchanging device structure is, can provide good heat exchange efficiency when occupying relative small size.
[0004] main purpose of the present invention provides a kind of heat exchanger that satisfies above-mentioned requirements.
[0005] other purposes of the present invention and advantage will be introduced below.
Summary of the invention
[0006] the present invention has realized above-mentioned purpose and advantage.
[0007] the invention provides a kind of refrigeration system, it comprises: compressor drives cold-producing medium in the fluid passage, the first pattern lower edge of system's operation at least; First heat exchanger, longshore current body passage is positioned at the downstream of compressor in first pattern; Second heat exchanger, longshore current body passage is positioned at the upstream of compressor in first pattern; With pressure regulator or expansion gear, its longshore current body passage in first pattern is positioned at the downstream of first heat exchanger and the upstream of second heat exchanger; Wherein: at least one comprises flat tube heat exchanger in described first heat exchanger and second heat exchanger.
[0008] heat exchanger that preferably limits of described flat tube heat exchanger by the single flat tube heat exchanger of serpentine bend.In addition, flat tube heat exchanger itself advantageously comprises the pipeline that is used for refrigerant conveying, wherein pipeline has height or reduced size and width or key dimension, and heat exchanger is set to minor face in the face of the flowing of heat transferring medium, and described heat transferring medium for example is an air.
Description of drawings
[0009] Fig. 1 is the schematic diagram of steam compression system;
[0010] Fig. 2 is the schematic diagram that has the box of single snake-like flat tube heat exchanger among the present invention;
[0011] Fig. 3 is CO
2The schematic diagram of gas compression system box;
[0012] Fig. 4 and Fig. 5 are the schematic diagrames of the single heat exchanger of flat tube single snake-like among the present invention;
[0013] Fig. 6 is the schematic diagram of the double adverse current serpentine heat exchanger of flat tube among the present invention;
[0014] Fig. 7 and Fig. 8 are the schematic diagrames of flat tube single snake-like evaporimeter among the present invention;
[0015] Fig. 9 a and 9b are the cross-sectional views of flat tube heat exchanger embodiment among the present invention.
The specific embodiment
[0016] the present invention relates to steam compression system, especially relate to and be used for this system, especially for the design of the heat exchanger tube of striding critical steam compression system, this to stride critical steam compression system for example be CO
2Working substance system.
[0017] striding critical CO
2In the refrigeration system, in order to keep peak efficiencies, key is to reduce the hot fluid at port of export place of high-side heat exchanger (gas cooler) and the temperature difference between the cold fluid.Compare with traditional HFC, because CO
2Density is higher, under given temperature, pressure and mass flow condition, for CO
2Refrigerant side heat exchange efficiency and pressure drop are littler.Therefore for CO
2Heat exchanger is necessary to have higher refrigerant mass fluxes, and this not only can improve CO
2Heat exchange efficiency, and can reduce CO
2Pressure.Yet, at restriction CO
2When pressure drops under a certain lower limit, should be able on the basis of total heat exchanger efficiency, improve net efficiency so that can obtain higher cycle efficieny.
[0018] in some application scenarios, in bottled drink or beverage cooler and other refrigeration plants, because air side dirt influence, is restricted with the additional air-side surface area of fin form, thereby limited total surface area.This needs heat exchanger to reduce the air side resistance and reduces the refrigerant side resistance significantly, described cold-producing medium such as CO
2
[0019] in addition, in the application of evaporimeter, in order to improve the reliability of total heat exchanger efficiency and raising compressor operating, heat exchanger should have the discharge of uniform cold-producing medium distribution and gratifying condensed fluid.
[0020] heat exchanger combines following advantage: plane surface, list/a plurality of inlets, single snakelike, many row, adverse current, cross-current, high heat transfer efficient, low cost, suitable material, corrosion-resistant, high burst strength, be easy to make and reduce air drag, above-mentioned advantage helps to obtain CO
2The constraint of the size of bottle cooler refrigeration system, efficient, expense and reliability.
[0021] one of method that improves total heat exchanger efficiency is to have flat tube heat exchanger.
[0022] refrigeration system 10 shown in Figure 1 has compressor 12, heat release heat exchanger 14 under the common operating condition, shown in Fig. 1 arrow, this heat exchanger is a downstream heat exchanger when observing with respect to compressor 12, expansion valve 16 is positioned at the downstream of heat exchanger 14, and heat absorption heat exchanger 18 is positioned at the downstream of expansion valve 16.The fluid of this system 10 is back to compressor 12 from heat exchanger 18.
[0023] Fig. 1 illustrates the first fluid 20 of heat transferring medium, as air, drives the heat exchanger 14 of flowing through by fan 22.This fluid is used for the heat that the absorption refrigeration agent is discharged, this cold-producing medium heat exchanger 14 of flowing through.
[0024] Fig. 1 also shows another air fluid 24, and this fluid is driven by fan 26 and flows through heat exchanger 18.This fluid 24 has been represented the part air in handling the space, and described air is flow through the refrigerant cools of heat exchanger 18.
[0025] as mentioned above, according to the present invention, provide a kind of improved heat exchanger tube structure, this structure is particularly useful for using transcritical refrigerant such as CO
2Steam compression system.
[0026] Fig. 2 shows a part of striding critical steam compression system 28, and shows compressor 12, heat exchanger 14 and the position of heat exchanger 18 in this special construction.
[0027] Fig. 3 is the side view of same structure, and shows compressor 12, heat exchanger 14 and heat exchanger 18 equally.
[0028] as described below, flat tube heat exchanger of the present invention provides the enhancing function in each space that is occupied by Tube Sheet of Heat Exchanger, and heat exchanger takies less space like can therefore being used for, thereby this part space that will save is as other purposes.For example, can find out significantly from Fig. 2 and Fig. 3 that flat tube heat exchanger of the present invention when design during as heat exchanger 14, is compared with a plurality of different assemblies of heat exchanger as shown in Figure 3, the single heat exchanger that can be used as shown in Figure 2 uses.
[0029] Fig. 4-8 shows the different embodiment of the flat tube heat exchanger described in the present invention.
[0030] Fig. 4 shows the schematic diagram of flat tube 30, this flat tube is shaped to roughly serpentine configuration as shown in the figure, and this flat tube is arranged for ease of admission of air stream 32, so that air flows along the long dimensional directions of flat tube 30, and therefore improve the heat exchange efficiency between the air flow mediums 32 and cold-producing medium in the flat tube 30.
[0031] Fig. 4 also shows fin 34, this fin can be advantageously provided from flat tube 30 extensions or otherwise be connected with flat tube heat exchanger of the present invention, so that flow extension in 32, and improved the exchange capability of heat between medium and the cold-producing medium at air.
[0032] Fig. 5 and Fig. 6 have further described flat tube heat exchanger of the present invention.Fig. 5 shows single flat tube heat exchanger, this heat exchanger construction becomes snakelike configuration or structure 36 roughly, make structure that single flat tube limits with snakelike mode bending, to limit a plurality of parts 37 or runner, these a plurality of parts 37 or runner are roughly parallel to each other.In the embodiment shown in fig. 5, identical with the embodiment of Fig. 4, be provided with single refrigerant inlet 38 and single refrigerant outlet 40 and handle the flow of refrigerant that flows through this structure 36.Structure 36 is advantageously provided and illustrated air fluid 39 interacts, and the narrow edge that more preferably is designed to flat tube 30 is in the face of entering fluid 39, and the long size or the width of flat tube are generally parallel with fluid 39.
[0033] as shown in the figure, flat tube heat exchanger of the present invention is limited by refrigerant tubing, and this refrigerant tubing has the profile of essentially rectangular, and has the inner fluid passage that limits, to be used for refrigerant conveying.
[0034] equally referring to Fig. 9 a and 9b, the profile of flat tube 46 is essentially rectangle.The profile of this essentially rectangular has relative minor face 47 and relative long limit 49, and the length that relative minor face 47 has is preferably between about 0.45 to about 4mm.Length that the relative long limit 49 or the size of rectangular profile preferably have or size are between about 12.7 to about 101.6mm.
[0035] equally shown in Fig. 7 and 8, it should be understood that the roughly snakelike structure 36 of flat tube heat exchanger of the present invention limits a series of substantially parallel fluid passages.According to the present invention, have been found that pipe apart from 50 or the pipeline of substantially parallel fluid passage between distance, as measuring, be preferably between the about 50mm of about 5-from horizontal center to center.Shown in Fig. 4 and 7, fin preferably if possible is set in the position of needs to strengthen heat exchange.In the time might comprising fin, the density of preferred this fin setting reaches about 20 fins/inch.
[0036] as can be seen from Figure 6, it is apparent that also snakelike basically flat tube heat exchanger structure 36 can be designed to many row's structures 42,44,, and then flow through second row 44 so that air fluid 39 flows through first row 42.On this aspect,, preferably these rows' array pitch 52 or the distance between each row center and another row center are arranged between about 12.7 to about 50mm according to the present invention.According to the present invention, heat exchanger can be arranged to about at least 20 rows, and the best effects that can reach according to the present invention.
[0037] as mentioned above, the internal fluid channels of the cold-producing medium of the inside of flat tube heat exchanger qualification can have multiple different shape.Fig. 9 a and 9b show two embodiment.In the embodiment shown in Fig. 9 a, in cross section shown in the flat tube 46 of the present invention, the entire inner space of flat tube 46 is provided for refrigerant fluid.
[0038] on the other hand, Fig. 9 b illustrates the flat tube 46 with fluid passage, described fluid passage is defined as one group of circular basically fluid passage 48, is 5 circular fluid passages in the present embodiment, and extend with the length direction of substantially parallel relation along flat tube 46 this fluid passage.
[0039] as mentioned above, this heat exchanger provides higher total heat exchange efficiency, and this is because the higher (CO thus of refrigerant mass fluxes
2Heat transfer efficiency is higher) thus and owing to compare with traditional pipe and to flow through the resistance that flat tube reduced air side and obtain lower air wide pre. drop.Based on the fluid cross-section area of flat tube, the total length of flat tube can be arranged to make CO
2Pressure drop be lower than an acceptable lowest limit, this lowest limit can access higher cycle efficieny under the certain limit service condition.
[0040] in addition, when as evaporator operation, single-cycle use (inlet and an outlet) can be eliminated CO
2Distribute uneven phenomenon, this phenomenon occurred in the heat exchanger (existing or flat tube) with a plurality of entrance and exits originally.In addition, described heat exchanger orientation should followingly be provided with, and pipeline is arranged in the vertical plane as shown in Figure 4, and fin can be provided with groove/opening.This can guarantee that condensate liquid discharges satisfactorily from flat tube and fin surface, otherwise this just becomes the limiting factor that flat tube heat exchanger is used as evaporimeter.
[0041] flat tube heat exchanger can have one or more inlet.A plurality of inlets help the high operating pressure of opposing and stride critical CO
2The inherent characteristic of vapor compression refrigeration system, and reduced CO
2Thereby pressure drop therefore help to improve hot property.
[0042] described flat tube (single inlet or multiple entry) can be easily with copper or aluminium or the making of other suitable materials, and these materials can bear strides critical CO
2The high fracture pressure of refrigeration system, and can be at one end or two ends be bent and/or weld, to form a continuous serpentine heat exchanger as shown in the figure.Fin can mechanical connection or is welded on the flat horizontal surface of pipe.In addition, can handle (applying coating or heating or the like) to the material of pipe and/or fin, to improve the resistance to corrosion of described heat exchanger.
[0043] in other design, arranging the flat tube single snake-like heat exchanger can interconnect more, and up to the independent circulation of acquisition, and fluid flows into another comb road to be similar to (air and CO from a comb road
2Between) counter-flow arrangement, this counter-flow arrangement is used to acquire high efficiency knownly.Counter-flow arrangement is to CO
2Gas cooler is extremely important, because the thermograde between the fluid of hot and cold must minimize, to keep the peak value cycle efficieny.
[0044] this heat exchanger is for CO
2The application of bottle cooler is very useful, and wherein the design of this heat exchanger is limited by space and expense greatly, and existing tubular type plate-fin heat exchanger can not provide feasible solution.
[0045] the present invention is particularly useful for compact business-use refrigrating system such as bottle cooler etc.
[0046] the heat exchanger typical case of existing steam compression system is a pipe fin type heat exchanger, and caliber is 1-7mm or bigger.For striding critical CO
2Steam compression system, this tube efficiency is low because with traditional HFC cold-producing medium such as R143, R404a etc. relatively, CO
2The density height.As everyone knows, flat tube (multiple entry) heat exchanger is long-pending more much smaller than the fluid cross-section of traditional round heat exchange of heat pipe, to reduce the air side flow resistance and to improve the heat exchange efficiency of refrigerant side.But the application of this heat exchanger is subjected to the technical problem restriction, these technical problems comprise that cold-producing medium distributes uneven, condensate liquid to discharge that property is poor, rupture strength reduces, cross flow one is arranged, cost is high and assembling is complicated, includes, but are not limited to following problem: use the low material of heat-conductive characteristic on the welding of costliness when multitube is connected to the arbitrary end of collector tube, the surface that fin is welded to pipe and for welding easily.
[0047] this kind heat exchanger is being striden critical CO
2Usefulness seldom in the bottle cooler system, in this system, minimum thermograde is very crucial for keeping peak efficiencies between the hot and cold fluid of the outlet of gas cooler (high-side heat exchanger).
[0048], still can obtain high CO for the bottle cooler evaporimeter
2Heat transfer efficiency and reduction CO
2In the time of pressure drop, the single snake-like vertical tube configuration has been eliminated the major technology problem, for example distributes uneven and the condensate liquid discharge, and these problems will limit for example use of evaporimeter of this heat exchanger.
[0049] described heat exchanger combines following advantage: plane surface, single or multiple inlet, single snake-like, many rows, high heat exchange efficiency, low cost, suitable material, corrosion resistance, high rupture strength, conveniently make and reduce air drag, these advantages help the requirement of acquisition bottle cooler refrigeration systems to size, efficient, expense and reliability.
[0050] compact nature of flat surface heat exchanger can allow to change the physical location of heat exchanger in the beverage cooler, thereby reduces the total area occupied of beverage cooler when keeping or improving system effectiveness.For example, high-side heat exchanger can move to other position, thereby has obtained added space, and this space can be used for other purpose, for example is used for air control of carrying out cold or hot surface etc.
[0051] compact nature of described heat exchanger also can cause reducing the amount of cold-producing medium or the charging amount in the refrigeration system, and therefore reduction expense, and this is very restricted in bottle cooler is used.
[0052] as mentioned above, the scope of described flat tube heat exchanger different size can be: pipe width or the main 12.7mm-101.6mm of being of a size of; Pipe height or the less 0.5mm-4mm that is of a size of; Single or a plurality of inlets, circular or non-circular inlet, the fluid hydraulic radius is 0.1mm-3mm; The distance of horizontal center to center is 5mm-50mm between tube pitch or the pipe; Between row spacing or the pipe longitudinally the distance of center to center be 12.7mm-50mm, fin density is a 0-20 fin per inch, single or many rows are 20.
[0053] an optimum embodiment of bottled drink or beverage cooler application mesohigh side heat exchanger or gas cooler has, and manages wide 25.4mm, and pipe highly is 2.0mm, 12 circular ports, 1.0mm port hydraulic radius, the tube pitch of 12.7mm, 4 fins of per inch, single row heat exchanger.
[0054] one or more embodiment of the present invention has been described.But should be appreciated that, under the situation that does not break away from the spirit and scope of the present invention, can carry out various modifications.For example, when making existing system or redesign existing system structure again, the details of existing structure can influence the details of its enforcement.Therefore, other embodiment are in the scope of the appended claim in back.
Claims (18)
1. refrigeration system comprises:
Compressor drives cold-producing medium in the fluid passage, the first pattern lower edge of system's operation at least;
First heat exchanger, longshore current body passage is positioned at the downstream of compressor in first pattern;
Second heat exchanger, longshore current body passage is positioned at the upstream of compressor in first pattern; With
Pressure regulator or expansion gear, its longshore current body passage in first pattern is positioned at the downstream of first heat exchanger and the upstream of second heat exchanger;
Wherein: at least one comprises flat tube heat exchanger in described first heat exchanger and second heat exchanger.
2. the system as claimed in claim 1, wherein: described flat tube heat exchanger comprises the pipeline of the profile with substantial rectangular, and at least one the internal flow port that is used for the refrigerant conveying fluid.
3. system as claimed in claim 2, wherein: the profile of described rectangle has minor face and long limit, and minor face flowing in the face of heat exchanging fluid is arranged in described fluid passage.
4. system as claimed in claim 3, wherein: described bond length is between about 0.5 to about 4.0mm, and the length that described long limit has is between about 12.7 to about 101.6mm.
5. system as claimed in claim 2, wherein: the hydraulic diameter that described pipeline has is between about 0.1 to about 3.0mm.
6. the system as claimed in claim 1, wherein: described flat tube heat exchanger comprises the flat tube of serpentine configuration, and it limits a plurality of substantially parallel fluid passages.
7. system as claimed in claim 6, wherein: described flat tube heat exchanger is arranged to have substantially parallel fluid passage, and this fluid passage is arranged in the vertical substantially plane.
8. system as claimed in claim 7, wherein: the fin density that fin presents reaches 20 fins of about per inch.
9. system as claimed in claim 6, wherein: the tube pitch that described serpentine configuration has is between about 5 to about 50mm.
10. the system as claimed in claim 1, wherein: described first heat exchanger comprises many row's flat tube heat exchanger, and row's spacing of described many rows is between about 12.7 to about 50mm.
11. the system as claimed in claim 1 also comprises: pass the fin that extend from described flat tube heat exchanger the fluid passage that is used for heat transferring medium.
12. the system as claimed in claim 1 also comprises: the fin that extends from described flat tube heat exchanger, and this fin has groove or opening, discharges to allow the condensate liquid on heat exchanger and the fin.
13. the system as claimed in claim 1, wherein: described flat tube heat exchanger has single inlet and single refrigerant outlet.
14. the system as claimed in claim 1, wherein: described flat tube heat exchanger comprises the flat tube of being made by copper or aluminium.
15. the system as claimed in claim 1, wherein: described flat tube heat exchanger comprises many row's flat tube heat exchanger assemblies, and this assembly is along the fluid passage setting of heat exchanging fluid, so that provide countercurrent flow between cold-producing medium in flat tube heat exchanger and the heat exchanging fluid.
16. as the described system of claim 0, wherein:
The main mass content of cold-producing medium comprises CO
2, and first and second heat exchangers are cold-producing medium-air heat exchanger.
17. the system as claimed in claim 1, wherein: described system is adapted to operate in strides under the critical both vapor compression pattern.
18. beverage cooling device that comprises the system as claimed in claim 1.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US66395705P | 2005-03-18 | 2005-03-18 | |
| US60/663,957 | 2005-03-18 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101142452A true CN101142452A (en) | 2008-03-12 |
Family
ID=37024107
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200580049152XA Pending CN101142452A (en) | 2005-03-18 | 2005-12-30 | Flat tube single snake-like co2 heat exchanger |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20080184734A1 (en) |
| EP (1) | EP1864060A4 (en) |
| JP (1) | JP2008533427A (en) |
| CN (1) | CN101142452A (en) |
| WO (1) | WO2006101565A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105371687B (en) * | 2015-10-27 | 2017-07-11 | 珠海格力电器股份有限公司 | Heat-exchanging component, heat exchanger and refrigeration system |
| CN108072285A (en) * | 2017-12-06 | 2018-05-25 | 广东美的制冷设备有限公司 | Radiation recuperator, air conditioner indoor unit and air conditioner |
| CN110617669A (en) * | 2012-07-06 | 2019-12-27 | 三星电子株式会社 | Refrigerator with a door |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008261615A (en) * | 2007-03-16 | 2008-10-30 | Mitsubishi Electric Corp | Heat exchanger, heat exchange device, refrigerator and air conditioner |
| DE102008043920A1 (en) * | 2008-11-20 | 2010-05-27 | BSH Bosch und Siemens Hausgeräte GmbH | Condensation dryer with a heat pump and method for its operation |
| FR2939187B1 (en) * | 2008-12-01 | 2013-02-22 | Valeo Systemes Thermiques | SPIRE HEAT EXCHANGER AND AIR CONDITIONING DEVICE COMPRISING SUCH A HEAT EXCHANGER |
| US20110024083A1 (en) * | 2009-07-31 | 2011-02-03 | Steimel John C | Heat exchanger |
| FR2963418B1 (en) * | 2010-07-28 | 2014-12-26 | Muller & Cie Soc | HEAT PUMP EXCHANGER |
| TWI809691B (en) * | 2022-01-27 | 2023-07-21 | 魏均倚 | Shaped tube cooling and cooling system |
| CN114777549B (en) * | 2022-06-20 | 2022-09-20 | 甘肃蓝科石化高新装备股份有限公司 | Finned tube with tube-fin bridge for gas to flow in different regions |
Family Cites Families (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3768554A (en) * | 1968-06-10 | 1973-10-30 | Westinghouse Electric Corp | Steam generator heated with liquid metal |
| JP3355824B2 (en) * | 1994-11-04 | 2002-12-09 | 株式会社デンソー | Corrugated fin heat exchanger |
| US6105386A (en) * | 1997-11-06 | 2000-08-22 | Denso Corporation | Supercritical refrigerating apparatus |
| DE19753601A1 (en) * | 1997-12-03 | 1999-06-10 | Behr Gmbh & Co | Cold storage, in particular for a motor vehicle |
| US6244330B1 (en) * | 1998-11-16 | 2001-06-12 | Foster Wheeler Corporation | Anti-vibration ties for tube bundles and related method |
| JP2000304472A (en) * | 1999-04-23 | 2000-11-02 | Calsonic Kansei Corp | Freezing cycle heat exchanger |
| JP2001012821A (en) * | 1999-06-25 | 2001-01-19 | Denso Corp | Serpentine type evaporator |
| US6182461B1 (en) * | 1999-07-16 | 2001-02-06 | Carrier Corporation | Photocatalytic oxidation enhanced evaporator coil surface for fly-by control |
| JP4186359B2 (en) * | 1999-12-07 | 2008-11-26 | 三菱電機株式会社 | HEAT EXCHANGER AND AIR CONDITIONING REFRIGERATOR HAVING THE HEAT EXCHANGER |
| JP2001330389A (en) * | 2000-05-19 | 2001-11-30 | Zexel Valeo Climate Control Corp | Heat exchanger |
| JP2002048421A (en) * | 2000-08-01 | 2002-02-15 | Matsushita Electric Ind Co Ltd | Refrigerating cycle system |
| DE10049256A1 (en) * | 2000-10-05 | 2002-04-11 | Behr Gmbh & Co | Serpentine heat exchanger e.g. evaporator or condenser/gas cooler for automobile air-conditioning, has link sections between corresponding pipe sections of different serpentine pipe blocks |
| JP4041654B2 (en) * | 2001-01-31 | 2008-01-30 | カルソニックカンセイ株式会社 | Louver fin of heat exchanger, heat exchanger thereof, and method of assembling the louver fin |
| EP1389721A1 (en) * | 2001-05-23 | 2004-02-18 | Matsushita Electric Industrial Co., Ltd. | Refrigerating cycle device |
| US6823932B2 (en) * | 2001-05-25 | 2004-11-30 | Modine Manufacturing Company | Self-fixturing side piece for brazed heat exchangers |
| DE10137907A1 (en) * | 2001-08-02 | 2003-02-20 | Modine Mfg Co | Air cooled heat transfer arrangement |
| US20030183378A1 (en) * | 2002-04-02 | 2003-10-02 | Memory Stephen B. | Heat exchanger and folded tube used therein |
| TWI261513B (en) * | 2002-04-30 | 2006-09-11 | Carrier Comm Refrigeration Inc | Refrigerated merchandiser with foul-resistant condenser |
| JP4080352B2 (en) * | 2003-02-26 | 2008-04-23 | 三菱電機株式会社 | Fin tube heat exchanger manufacturing method and air conditioning refrigeration system |
-
2005
- 2005-12-30 CN CNA200580049152XA patent/CN101142452A/en active Pending
- 2005-12-30 US US11/908,754 patent/US20080184734A1/en not_active Abandoned
- 2005-12-30 JP JP2008501865A patent/JP2008533427A/en active Pending
- 2005-12-30 WO PCT/US2005/047527 patent/WO2006101565A1/en active Application Filing
- 2005-12-30 EP EP05856007A patent/EP1864060A4/en not_active Withdrawn
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110617669A (en) * | 2012-07-06 | 2019-12-27 | 三星电子株式会社 | Refrigerator with a door |
| CN110617669B (en) * | 2012-07-06 | 2021-10-08 | 三星电子株式会社 | Refrigerator with a door |
| CN105371687B (en) * | 2015-10-27 | 2017-07-11 | 珠海格力电器股份有限公司 | Heat-exchanging component, heat exchanger and refrigeration system |
| CN108072285A (en) * | 2017-12-06 | 2018-05-25 | 广东美的制冷设备有限公司 | Radiation recuperator, air conditioner indoor unit and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2006101565A1 (en) | 2006-09-28 |
| JP2008533427A (en) | 2008-08-21 |
| EP1864060A4 (en) | 2010-09-29 |
| US20080184734A1 (en) | 2008-08-07 |
| EP1864060A1 (en) | 2007-12-12 |
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