CN101111734B - Parallel flow heat exchangers incorporating porous inserts - Google Patents

Parallel flow heat exchangers incorporating porous inserts Download PDF

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Publication number
CN101111734B
CN101111734B CN2005800476873A CN200580047687A CN101111734B CN 101111734 B CN101111734 B CN 101111734B CN 2005800476873 A CN2005800476873 A CN 2005800476873A CN 200580047687 A CN200580047687 A CN 200580047687A CN 101111734 B CN101111734 B CN 101111734B
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China
Prior art keywords
heat exchanger
parallel flow
flow heat
porous member
passage
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Expired - Fee Related
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CN2005800476873A
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Chinese (zh)
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CN101111734A (en
Inventor
M·F·塔拉斯
A·C·柯克伍德
R·A·乔普科
R·A·小拉斯特
M·B·戈尔布诺夫
I·B·韦斯曼
P·费尔马
T·D·拉德克利夫
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Carrier Corp
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Carrier Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof

Abstract

A parallel flow (minichannel or microchannel) evaporator includes a porous member inserted at the entrance of the evaporator channels which provides refrigerant expansion and pressure drop controls resulting in the elimination of refrigerant maldistribution and prevention of potential compressor flooding.

Description

Parallel flow heat exchanger with porous insert
The cross reference of related application
The application relates to and requires the U.S. Provisional Application No.60/649 of application on February 2nd, 2005,425, title is the priority of " PARALLEL FLOW EVAPORATOR INCORPORATINGPOROUS CHANNEL INSERTS (the parallel type evaporimeter with porous type passage insert) ", and the full text that is incorporated herein this application as a reference.
Technical field
Present invention relates in general to air-conditioning, heat pump and refrigerating system, more especially, relate to the parallel type evaporimeter of these systems.
Background technology
The definition of so-called parallel flow heat exchanger is widely used in air-conditioning and the refrigeration industry, and point out that heat exchanger has a plurality of parallel channels, in this parallel channels, refrigerant distributes with the direction that is basically perpendicular to the flow direction of this refrigerant in inlet header and outlet header and flows into.This is defined in the technos and generally is suitable for, and will be used to this paper in full.
The bad distribution of refrigerant in the evaporimeter of refrigerating system is well-known phenomenon.It has caused the obvious reduction of evaporimeter and overall system performance in very big condition of work scope.The appearance of the bad distribution of refrigerant may be owing to uneven airflow distribution, unsuitable heat exchanger orientation or collector and distribution system design of poor quality on the difference of the flow resistance of boiler channel inside, the external heat transfer surfaces.Bad distribution especially appears in the parallel type evaporimeter, this be since they for refrigerant enter each refrigerant circuits specific design.In order to eliminate or reduce trial that this phenomenon done the influence of parallel type performance of evaporator seldom or not success.The main cause of these failures usually with the complexity and the poor efficiency or relevant of proposition technology with the high cost of this scheme.
In recent years, be not only at automotive field and at heating, ventilation, air-conditioning and refrigeration (HVAC﹠amp; R) in the industry, parallel flow heat exchanger---aluminium heater of particularly furnace brazing (furnace-brazed)---has been subjected to many concerns and attention.The main cause of use parallel type technology is relevant with the corrosion resistance of the compactedness of its superior performance, height and enhancing.Parallel flow heat exchanger uses now in the condenser and evaporimeter of multiple product and system's design and structure.Although bigger benefit and benefit are arranged, the application of evaporimeter still has a lot of challenges and difficulty.The bad distribution of refrigerant is main an influence and obstacle of carrying out this technology in evaporator application.
As is known, the bad distribution of refrigerant occurring in parallel flow heat exchanger is because in channel interior and pressure drop different in import and outlet header and collector and distribution system design of poor quality.In collector, difference in length, the thing of refrigerant paths is separated (phaseseparation) and gravity is the principal element that causes bad distribution.In heat exchanger channel inside, the variation of rate of heat transfer, airflow distribution, manufacturing tolerance and gravity are principal elements.In addition, the recent trend that heat exchanger performance strengthens is the miniaturization (so-called passage aisle and microchannel) that improves its passage, and this has influenced the distribution of refrigerant again unfriendly.Because the control all of these factors taken together is very difficult, all failed so much control the effort of refrigerant distribution (the particularly refrigerant distribution in the parallel type evaporimeter) before.
In the refrigerating system that uses parallel flow heat exchanger, import and outlet header or header (use in this article of these terms is interchangeable) have the shape of a common cylindrical shaped usually.When two-phase flow entered this header, vapour phase was normally with liquid phase separation.Because these two kinds of things flow mutually independently, so the bad distribution of refrigerant can occur.
If this two-phase flow is to enter this inlet header than higher speed, then the momentum by this flow carries this liquid phase arrives this header away from this collector inlet distal part.Therefore, the passage of the most close this collector inlet mainly receives vapour phase, and mainly receives liquid phase away from the passage of this collector inlet.On the other hand, if it is very low to enter the speed of two-phase flow of this collector, then there is not sufficient momentum to carry liquid phase along this header.As a result, liquid phase enters the passage of close import, and vapour phase enters passage farthest.Equally, the liquid in this inlet header can be used for separating with steam by gravity, has caused similar bad distribution consequence.In both of these case, bad distribution phenomenon presents in evaporimeter soon and has reduced overall system performance.
In addition, bad distribution phenomenon can cause two-phase (zero superheat) state in the exit of some passages, forms potential overflow (flooding) at the compressor suction place, and it can transfer the fault of compressor soon to.
Summary of the invention
Therefore, the purpose of this invention is to provide the system and method that overcomes above-mentioned prior art problems.
The objective of the invention is to be that parallel type (microchannel or passage aisle) evaporimeter introduces pressure drop control, it is the pressure drop on the balance heat exchanger flow circuit basically, and has therefore eliminated bad distribution of refrigerant and the problem relevant with it.Further, the objective of the invention is provides refrigerant to expand in the porch of each passage, thereby eliminates main two-phase flow (two-phase flow is the one of the main reasons that causes the bad distribution of refrigerant) in inlet header.Have been found that and in each passage of parallel type evaporimeter, insert porous media or introduce porous media, then realized these purposes in the porch of each passage of parallel type evaporimeter.For example, during whole heat exchanger is carried out furnace brazing, these porous media inserts can soldering in each passage, chemically bonding or in place with mechanical method fixation.In addition, use for low cost, these inserts are used as mainly (and being unique) expansion gear, perhaps, in the situation of the accurate thermal control excessively of needs, thermostatic expansion valve (TXV) or electric expansion valve (EXV) are used as main expansion gear, and these inserts are as less important expansion gear.
Can use any suitable porous insert that to realize above-mentioned purpose.Suitable and cheap porous insert can be made by sintering metal, compressed metal, such as steel wool, custom-designed porous ceramics or the like.When placing cheap porous media insert in each passage at the parallel type evaporimeter or in the porch of each passage of parallel type evaporimeter, it presents the main resistance to the flow of refrigerant in the evaporimeter.In such a case, main pressure drop zone will appear on these inserts, and in the passage of parallel type evaporimeter or the change in pressure drop in the collector will play the part of the role of less important (inessential).Further, expand, account for main single-phase liquid refrigerant and flow through this inlet header because refrigerant takes place in the porch of each passage, when this porous insert during as main and unique expansion gear especially like this.So just obtained uniform refrigerant distribution, improved the performance of evaporimeter and system, simultaneously, do not lost accurately and to cross thermal conditioning when needing (as long as).In addition, the very low cost of the method that proposes haves a great attraction the present invention.
Description of drawings
In order further to understand purpose of the present invention, in conjunction with the accompanying drawings with reference to following detailed description of the invention, wherein:
Fig. 1 is the schematic diagram according to the parallel flow heat exchanger of prior art.
Fig. 2 is the fragmentary side cross-sectional view of one embodiment of the present of invention.
Fig. 3 is the end-view that is positioned at the porous insert at feeder connection place of the present invention.
Fig. 4 is the perspective view of the porous insert shown in Fig. 3.
Fig. 5 a is the side cut away view of another embodiment of the present invention.
Fig. 5 b is the side cut away view of further embodiment of this invention.
Fig. 6 is the end-view of a plurality of passages in the one embodiment of the invention.
Fig. 7 a is the perspective view that perforated lid embodiment of the present invention is shown.
Fig. 7 b is the perspective view that the second perforated lid embodiment is shown.
Fig. 7 c is the perspective view that the 3rd perforated lid embodiment is shown.
The specific embodiment
With reference to Fig. 1, as an example, illustrated parallel type (microchannel or passage aisle) heat exchanger 10 comprises inlet header or collector 12, outlet header or collector 14 and a plurality of passage that is arranged in parallel 16, and these passages 16 are connected to outlet header 14 with inlet header 12 fluids.Usually, this inlet header 12 and outlet header 14 are columniform, and this passage 16 is the pipes (or extrusion modling thing) with flat or circular cross section.Passage 16 has a plurality of inside and outside heat transfer enhancement elements usually, such as fin.For example, the outside fin 18 of furnace brazing (furnace-brazed) is arranged usually, these outside fin 18 are evenly arranged between the passage and are used to strengthen the heat exchanging process and the rigidity of structure.Passage 16 also can have internal heat transfer to be strengthened and structural detail.
At work, refrigerant flows into this inlet 20 and enters in the internal cavities 22 of inlet header 12.Become liquid, steam or liquid and steam mixture (to have at evaporimeter under the occasion of the expansion gear that is positioned at the upstream, this is most typical situation) refrigerant of form is from these internal cavities 22 admission passage openings 24, so that enter in the internal cavities 26 of this outlet header 14 through this passage 16.Refrigerant flows out this outlet 28 from this internal cavities 26 (under the situation of evaporator application, this refrigerant is generally vapor form at this moment), enters the compressor (not shown) then.Outside at passage 16, make air on passage and related fin 18, flow (preferably evenly flowing) by air-supply arrangement (as the fan (not shown)), so that between the air of passage flows outside and the refrigerant in the passage, carry out heat transmission interaction.
According to one embodiment of present invention, insert porous insert 30 in the porch of each passage 16.When passage 16 has internal structural element such as support unit 16a (Fig. 3) (normally be used to improve the rigidity of structure and/or strengthen the purpose that heat is transmitted), and when support unit 16a is positioned at the porch of passage, this porous insert 30 has groove 32, to hold this support unit 16a.Further, provide in various degree expansion and/or hydraulic resistance if wish by insert 30 or 32, above-mentioned other factors of refrigerant distribution of 16 in these passages for example are used to offset an influence, can change insert such as porosity value or physical dimension characteristics such as (the insert degree of depth, insertion depths etc.), so that be that each passage 16 obtains required effects.
Fig. 5 a shows another embodiment, and wherein, whole inlets of these passages 16 are covered by the single porous member 34 that is positioned at collector 40.Further, can use support unit 36 in collector 40, to assist to set up the relative position of porous member 34 and passage 16.Should be noted that the assembly that is made of porous member 34 and support unit 36 can be made for and be combined into the single part that is made of porous materials.
Fig. 5 b is the further embodiment of the structure among Fig. 5 a, and wherein, this porous member is the compound of two kinds of different porous materials 34 and 34a.Obviously, the quantity of the composite in this porous member can be more than two kinds.
Fig. 6 shows the side view of Fig. 5 a.
Fig. 7 a shows unitized elongated porous member 34b, and it is sealing a plurality of passages 16 from feeder connection preset distance place.
Fig. 7 b shows a kind of elongated porous member 34c, and it has covered the end of a plurality of passages 16.
Fig. 7 c is the improvement to Fig. 7 b structure, wherein, porous member 34d is in the end that covers passage 16 in shape exactly. and the shape of this porous member 34d can have any suitable structure, but not rectangular cross section. further, this porous member 34d is preferably between the inwall that is positioned so that collector 40 in the collector 40 and the porous member 34a gapped, thereby allows refrigerant before entering this porous member 34d and passage 16 more uniform distribution to be arranged.
Should be appreciated that, can use the porous member and/or the material of any kind that can realize the object of the invention.Equally, to shown in Figure 7, any design of the object of the invention or structure of realizing can be applied in the use of the present invention as Fig. 2.
And it is also noted that in condenser and evaporator application, this porous insert also can be used in the intermediate header.For example, if heat exchanger has more than one refrigerant pathway, then in the design of this heat exchanger, add intermediate header (between inlet header and outlet header).In intermediate header, refrigerant generally exists with the two-phase state, and this heat exchanger structure can be benefited from the present invention by the porous insert being joined in this intermediate header equally.And, in order only to provide fluid resistance uniformity and pressure drop control, the porous insert can be put into the inlet header of condenser and the outlet header of evaporimeter, and the influence of heat exchanging device overall performance is less.
For application-specific, because causing the various factors of the bad distribution of the refrigerant in the admission passage 16 has just known in the design phase usually, the inventor has been found that can introduce these design features offsets these factors, so that eliminate their adverse effects, and eliminate the compressor overflow and the fault that might take place to evaporimeter and overall system performance.For example, under many circumstances, know that usually refrigerant is with high speed or low the inflow in this inlet header, and know these velocity amplitudes are how to influence this bad distribution phenomenon.Person of skill in the art will appreciate that how instruction of the present invention is applied in other the system performance.
Although illustrate and described the present invention with reference to the preference pattern that goes out as shown in drawings, but those skilled in the art should understand, under the situation that does not break away from the spirit and scope of the present invention that are defined by the claims, various variations can be arranged in details and configuration aspects.

Claims (40)

1. parallel type passage aisle or micro-channel heat exchanger comprise:
The inlet header that extends longitudinally, this inlet header have and are used to guide fluid to flow to into the inlet of described inlet header and are used for along a plurality of outlets of transverse guidance from the fluid stream of described inlet header;
A plurality of passages, each passage all has feeder connection, and these a plurality of passages are arranged with substantially parallel relation, and fluid is connected to described a plurality of outlet, are used to guide the fluid stream from described inlet header; With
Outlet header, this outlet header fluid is connected to described a plurality of passage, is used to receive the fluid stream from this passage;
Wherein, described heat exchanger comprises at least one porous member of settling across each the entire flow path in described a plurality of passages, and thus, described heat exchanger shows the remarkable bad distribution of described a plurality of interchannel flows that reduced.
2. parallel flow heat exchanger as claimed in claim 1, wherein, described heat exchanger is an evaporimeter.
3. parallel flow heat exchanger as claimed in claim 1, wherein, described heat exchanger is a condenser.
4. parallel flow heat exchanger as claimed in claim 1, wherein, the form of described porous member is arranged on the insert at least one passage.
5. parallel flow heat exchanger as claimed in claim 4, wherein, described porous insert is positioned in the feeder connection place.
6. parallel flow heat exchanger as claimed in claim 5, wherein, this porous insert is positioned to contiguous this feeder connection.
7. parallel flow heat exchanger as claimed in claim 5, wherein, this porous insert is positioned in the inside of this passage.
8. parallel flow heat exchanger as claimed in claim 1, wherein, this porous member is positioned in this inlet header or becomes direct fluid to be communicated with this inlet header.
9. parallel flow heat exchanger as claimed in claim 1, wherein, this porous member is positioned in this outlet header or becomes direct fluid to be communicated with this outlet header.
10. parallel flow heat exchanger as claimed in claim 1, wherein, this porous member is positioned at least one described collector or becomes direct fluid to be communicated with at least one described collector.
11. parallel flow heat exchanger as claimed in claim 1, wherein, the material of making described porous member is selected from metal and pottery.
12. parallel flow heat exchanger as claimed in claim 1, wherein, the material of making described porous member is selected from: sintering metal, compressed metal, metal wool or metal wire.
13. parallel flow heat exchanger as claimed in claim 1, wherein, described porous member is longitudinally settled along collector.
14. parallel flow heat exchanger as claimed in claim 1 is wherein, gapped between described porous member and collector inner wall surface.
15. parallel flow heat exchanger as claimed in claim 1, wherein, described porous member is the compound that is made of at least two kinds of different inserts.
16. parallel flow heat exchanger as claimed in claim 1, wherein, the cross section of described porous member is a non-rectangle.
17. parallel flow heat exchanger as claimed in claim 16, wherein, the cross section of described porous member is the part of circle.
18. parallel flow heat exchanger as claimed in claim 1, wherein, described porous member has characteristic variable between at least two passages.
19. parallel flow heat exchanger as claimed in claim 1, wherein, the Performance Characteristics of this porous member can change by at least one that control in porosity, the degree of depth, insertion depth and the material.
20. parallel type passage aisle or micro-channel heat exchanger comprise:
The inlet header that extends longitudinally, this inlet header have and are used to guide fluid to flow to into the inlet of described inlet header and are used for along a plurality of outlets of transverse guidance from the fluid stream of described inlet header;
A plurality of passages, each passage all has feeder connection, and these a plurality of passages are arranged with substantially parallel relation, and fluid is connected to described a plurality of outlet, are used to guide the fluid stream from described inlet header; With
Outlet header, this outlet header fluid is connected to described a plurality of passage, is used to receive the fluid stream from this passage;
Wherein, described heat exchanger comprises at least one porous member of settling across each the entire flow path in described a plurality of passages, wherein, described porous member is designed at least one in expansion control in this system and the pressure drop control, and wherein, described heat exchanger shows the remarkable bad distribution of described a plurality of interchannel flows that reduced.
21. parallel flow heat exchanger as claimed in claim 20, wherein, described heat exchanger is an evaporimeter.
22. parallel flow heat exchanger as claimed in claim 20, wherein, described heat exchanger is a condenser.
23. parallel flow heat exchanger as claimed in claim 20, wherein, this porous member is as main expansion gear.
24. parallel flow heat exchanger as claimed in claim 20, wherein, this porous member is as less important expansion gear.
25. parallel flow heat exchanger as claimed in claim 20, wherein, the form of described porous member is arranged on the insert at least one passage.
26. parallel flow heat exchanger as claimed in claim 25, wherein, described porous member is positioned in the feeder connection place.
27. parallel flow heat exchanger as claimed in claim 26, wherein, this porous member is positioned to contiguous this feeder connection.
28. parallel flow heat exchanger as claimed in claim 26, wherein, this porous member is positioned in the inside of this passage.
29. parallel flow heat exchanger as claimed in claim 20, wherein, this porous member is positioned in this inlet header or becomes direct fluid to be communicated with this inlet header.
30. parallel flow heat exchanger as claimed in claim 20, wherein, this porous member is positioned in this outlet header or becomes direct fluid to be communicated with this outlet header.
31. parallel flow heat exchanger as claimed in claim 20, wherein, this porous member is positioned in the inlet header or becomes direct fluid to be communicated with this inlet header.
32. parallel flow heat exchanger as claimed in claim 20, wherein, the material of making described porous member is selected from metal and pottery.
33. parallel flow heat exchanger as claimed in claim 20, wherein, the material of making described porous member is selected from: sintering metal, compressed metal, metal wool or metal wire.
34. parallel flow heat exchanger as claimed in claim 20, wherein, described porous member is longitudinally settled along collector.
35. parallel flow heat exchanger as claimed in claim 20 is wherein, gapped between described porous member and collector inner wall surface.
36. parallel flow heat exchanger as claimed in claim 20, wherein, described porous member is the compound that is made of at least two kinds of different parts.
37. parallel flow heat exchanger as claimed in claim 20, wherein, the cross section of described porous member is a non-rectangle.
38. parallel flow heat exchanger as claimed in claim 37, wherein, the cross section of described porous member is the part of circle.
39. parallel flow heat exchanger as claimed in claim 20, wherein, described porous member presents Performance Characteristics variable between at least two passages.
40. parallel flow heat exchanger as claimed in claim 39, wherein, this variable Performance Characteristics depends at least one in porosity, the degree of depth, insertion depth and the material.
CN2005800476873A 2005-02-02 2005-12-29 Parallel flow heat exchangers incorporating porous inserts Expired - Fee Related CN101111734B (en)

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US64942505P 2005-02-02 2005-02-02
US60/649,425 2005-02-02
PCT/US2005/047310 WO2006083443A2 (en) 2005-02-02 2005-12-29 Parallel flow heat exchangers incorporating porous inserts

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CN101111734B true CN101111734B (en) 2010-05-12

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