CN101629792A - Fatigue-proof plate heat exchanger - Google Patents
Fatigue-proof plate heat exchanger Download PDFInfo
- Publication number
- CN101629792A CN101629792A CN200910151674A CN200910151674A CN101629792A CN 101629792 A CN101629792 A CN 101629792A CN 200910151674 A CN200910151674 A CN 200910151674A CN 200910151674 A CN200910151674 A CN 200910151674A CN 101629792 A CN101629792 A CN 101629792A
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- Prior art keywords
- exchangers
- heat
- plate type
- type
- passage
- 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.)
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Classifications
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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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
- F28D9/0068—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- 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
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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
- F28D2021/0049—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for lubricants, e.g. oil coolers
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Plate heat exchanger for indirect heat exchange between at least two liquid and/or gaseous media with an essentially parallelepiped-shaped base (8), means for feeding and removing the media (headers 6, 6a, 7), and a number of passages (14), arranged essentially like stacks, for indirect heat exchange between media that respectively flow into adjacent passages (14), whereby the passages are formed by partitions (1, 22) that are spaced some distance apart, whereby the partitions are spaced some distance apart by end strips (4a, 4b), the passages have a corrugated profile (fins, 2), which is in heat-conductive contact with the partitions (1, 22) at its wave peaks and wave troughs, and the stack is closed off by a cover plate (5, 21), characterized in that the ratio between the width of the partition (B) and the repetition interval of the same characteristic of the corrugated profile as, for example, the repetition interval of two wave peaks (wavelength, LP) has a value in the range of between 15 and 80.
Description
Technical field
The present invention relates to a kind of heat-exchangers of the plate type, be used for the indirect heat exchange between at least two media liquid and/or gaseous state, this heat-exchangers of the plate type has the matrix of rectangular parallelepiped shape basically, be used to infeed and discharge the device (collector of described medium, take over) and a plurality of passage that stacks the shape layout basically, these passages are used for making respectively between the medium that adjacent passage flows and carry out indirect heat exchange, wherein, these passages form by the demarcation strip of the distance that separates each other, wherein, these demarcation strips are by the sealing lath distance that separates each other, these passages have the wide part (fin) of wavy type, the wide part of described wavy type contacts with demarcation strip formation heat conduction with the trough place at its crest, and this stacks and passes through cover closure.Invention has been described with the example of oil cooler or aerial cooler, but the present invention also can be applicable to heat-exchangers of the plate type arbitrarily in theory, therefore is not limited to the application of exemplary description.
Background technology
Heat-exchangers of the plate type is by open with a large amount of forms of implementation and be designed to indirect heat exchange between at least two media liquid and/or gaseous state.Participate in the medium passage in this flows through this heat exchanger, that spatially be separated out of heat exchange, thereby only carry out heat exchange indirectly.At this, this indirect heat exchange is by making corresponding passage structure separated from one another, being that so-called demarcation strip carries out.
These demarcation strips are arranged in the heat exchanger and by the sealing lath with stacking shape and are spaced apart from each other.Form so-called passage thus between these demarcation strips, the MEDIA FLOW that participated in heat exchange at that time is through these passages.On the whole, these demarcation strips have the shape of substantial rectangular, thereby obtain the heat-exchangers of the plate type of approximate rectangular parallelepiped shape under the situation that stacks the shape layout.According to prior art, be provided with on the structure of rectangular parallelepiped shape basically at this and be used for device that corresponding medium is fed to different passages and discharges.
According to prior art, these passages have the wide part of wavy type, are so-called fin.Go into the wide part of wavy type in that these passages that form are mid-between demarcation strip, the described wavy wide part of type at the corresponding reversal point place of this wavy texture, be that so-called crest contacts with demarcation strip formation heat conduction with the trough place.At this, the wide part of wavy type is positioned to the flow direction perpendicular to the medium of the described passage of flowing through.Thus, contact the heat exchange of the medium that has improved two adjacency channels of flowing through with the heat conduction of demarcation strip at the reversal point place by the wide part of wavy type.
When this heat-exchangers of the plate type according to prior art was used as oil cooler or aerial cooler, the described device that is used to infeed and discharge was so constructed, feasible oil and these adjacent passages of alternately flowing through respectively as the air of cooling medium.If this cooler is used in compressor, then this heat-exchangers of the plate type often suffers pressure alternation and temperature alternating.This pressure alternation or temperature alternating cause high mechanical stress, and this causes high material load and fatigue of materials fast.
Summary of the invention
Therefore, task of the present invention is to design the heat-exchangers of the plate type that a kind of this paper starts described type like this, makes the physical dimension of this heat-exchangers of the plate type be optimized as follows, promptly improves stability and fatigue resistance.
Described task realizes in the following manner, promptly the repeat distance of the same characteristic features of the width of demarcation strip and the described wavy wide part of type, for example the ratio between the repeat distance (wavelength) between two crests has the interior value of scope between 15 and 80.
Beat allly be that the experimental and numerical by the reinforcement undertaken by Finite Element Method studies show that, can significantly improve the mechanical stability and the fatigue resistance of heat-exchangers of the plate type when changing the physical dimension of heat-exchangers of the plate type according to the present invention.Can not only significantly improve the stabilizer of heat exchanger by the ratio of the width of demarcation strip and wavelength being arranged on the value in the scope between 15 and 80, and significantly improve its fatigue resistance according to the present invention.Simulation as the heat-exchangers of the plate type of oil cooler shows that in according to form of implementation of the present invention, before fatigue fracture took place, fatigue resistance had on average been improved 10 times.
Basic design of the present invention is by the geometric parameter that the makes heat-exchangers of the plate type stability of improving suitably coordinated with each other.According to the present invention, not only all parts of this heat-exchangers of the plate type more massively (massiver) constitute improving its stability, and the ratio between wavelength and the demarcation strip width is optimized.According to the present invention, select calibration in this wise by the ratio adjusting of demarcation strip width and wavelength---how many wavy textures (fin) are set, feasible optimum stabilization and the fatigue resistance that realizes this heat-exchangers of the plate type on the demarcation strip of given width.
According to a favourable configuration of the present invention, the width of demarcation strip and the ratio between the wavelength have between 20 and 60, the value in the scope between preferred 28 and 50, between preferred especially 29 and 43.
What meet purpose is that the width of demarcation strip and the ratio between the thickness are less than 150.In a favourable configuration of the present invention, the width of demarcation strip and the ratio between the thickness have between 50 and 150, the value in the scope between preferred 75 and 115, between preferred especially 80 and 105.Realized the further improvement of stability and fatigue resistance with respect to the additional optimizations of demarcation strip thickness by the demarcation strip width.
Advantageously, when the oil that is used as medium at passage flows through, in the scope of ratio between 7 and 80 of the material thickness (fin thickness) of difference in height (fin height) between the minimum point of the peak of a crest and a trough and the described wavy wide part of type.In a configuration of the present invention, when the oil that is used as medium at passage flows through, in the scope of the ratio between fin height and the fin thickness between 8 and 20, between preferred 10 and 15.Be proved advantageously within the scope of the invention, when oily, constructed fin like this, made that the ratio between fin height and the fin thickness always is in a value between 8 and 20 the passage of heat exchanger guiding heat, to be cooled.
Be proved to be also advantageously, structure seals lath in this wise, make described sealing lath have a bottom surface and three fins perpendicular to this bottom surface, wherein, these three fins are orientated in this wise, make these fins point to the inside of the matrix of described rectangular parallelepiped shape, and the intermediate fins of these three fins is longer than two outside fins.At this, this sealing lath of the present invention can not only have an opening or breach but also can have a plurality of openings or breach, and described one/some corresponding media are directed in the described passage by described opening or breach.All distances between preferred two demarcation strips are sealed by such sealing lath respectively on two of described demarcation strip short limits.The quality of sealing lath can be reduced by three fins that stand vertically of structure on the bottom surface, mechanical stability can be do not damaged simultaneously.When using as oil cooler, two long limits advantageously do not have sealing lath ground formation and surrounding air is flow through as cooling medium.
In a particularly preferred configuration of the present invention, heat-exchangers of the plate type of the present invention is as oil cooler or aerial cooler, and wherein, particularly deep fat is cooled by carrying out heat exchange with air.In this application, heat-exchangers of the plate type is owing to the frequent temperature and/or the pressure variation that are caused by application conditions of oil to be cooled suffer extra high mechanical load.Under this applicable cases, the high mechanical stability that realizes by the present invention and fatigue resistance is particularly advantageous plays a role.
By the present invention, realized in this wise that particularly a kind of this paper starts the heat-exchangers of the plate type of described type, make particularly when using under the situation that continues variation at pressure dependence and temperature relation, compared with prior art significantly improved the mechanical stability and the fatigue resistance of heat-exchangers of the plate type.
Description of drawings
Elaborate the present invention by means of the embodiment that elaborates in the accompanying drawings of the present invention below.Wherein:
Fig. 1 illustrates the schematic perspective view of a form of implementation of heat-exchangers of the plate type of the present invention,
Fig. 2 illustrates the view identical with Fig. 1, wherein, does not have annex,
Fig. 3 a illustrates the schematic perspective view of a passage of the heat-exchangers of the plate type among Fig. 1 and 2,
Fig. 3 b illustrates the part figure of the cross section of the passage among Fig. 3 a,
Fig. 4 illustrates the disintegration figure of one second form of implementation of heat-exchangers of the plate type of the present invention with schematic perspective view.
The specific embodiment
Fig. 1 illustrates a heat-exchangers of the plate type from visual observation.This heat-exchangers of the plate type has the rectangular parallelepiped 8 of central authorities, and the length L of this rectangular parallelepiped is that 1.1m and its width B and height H are respectively 11cm.This above rectangular parallelepiped 8, the side and below can see the semi-cylindrical box installed (
) 6 and 6a (collector).A side of side also has this box of installing below this rectangular parallelepiped 8 and shown in deviate from.But they are partly hidden.Can infeed fluid or this fluid is taken out again this heat-exchangers of the plate type by taking over 7, be the sky G﹠O at this this fluid.Collector 6 and 6a are used for distributing the medium of introducing by described adapter 7 or are used to collect and are used for concentrating and treat the medium that takes out from this heat-exchangers of the plate type and (wall) with 8mm (collector 6) is thick or (wall) 6mm (collector 6a) is thick.
Heat-exchangers of the plate type shown in Fig. 1 is designed to make two above fluid streams to flow through to carry out heat exchange by each other in separated passage.The part of described stream can oppositely flow by each other, and another part intersects.In order to set forth the present invention, consider simple situation, promptly air stream and oil stream in separated, the passage that replaces each other across in that the next door is mobile each other.The fluid stream of greater number does not have to propose the viewpoint of additional matter within the scope of the invention.
How the inside of the heat-exchangers of the plate type among Fig. 1 constitutes as can be seen in Fig. 2.Rectangular parallelepiped 8 is made of demarcation strip 1 and wavy wide part 2 (fin) of type or the wide part 3 of distribution type basically.Layer with the wide part 2 of demarcation strip 1 and type or 3 replaces each other.Intermediate space between the demarcation strip 1 be called as passage 14 (such passage shown in Fig. 3 a and the 3b and below described), described demarcation strip is designed to be flow through by a fluid and have the wide part 2 and 3 of type at this.
This rectangular parallelepiped 8 is by on the face that scolder is applied to demarcation strip 1 and demarcation strip 1 and passage 14 are alternately piled up each other produce.Cover plate 5 hides this up or down and stacks 8.Then, stack by surrounding this that heating makes this stack 8 welding in 8 the stove at one.
Distribute the wide part 3 of type on the side of this heat-exchangers of the plate type, to have the wide part inlet 9 of the type of distribution (also referring to Fig. 2, the breach among sealing strip 4a and the sealing lath 4b).Distribute the wide parts inlet of types by these, fluid can and be taken over 7 via collector 6 and 6a and enter into corresponding passage 14 from the outside or be removed again.Distribute the wide part inlet 9 of type in Fig. 1, to be hidden shown in figure 2 by collector 6 and 6a.
In these passages 14 of the heat-exchangers of the plate type shown in Fig. 1 and 2 shown in Fig. 3 a one.The flow direction of fluid is represented by arrow.Fluid distributes the wide part of type 9 places that enter the mouth to flow at one, so that be distributed on the whole width of passage 14 in the wide part 3 of the distribution type of correspondence.Then, this fluid distribution type exterior feature part of flowing through the wide part 2 of heat exchange type wavy and focusing on outlet side from the wide part 3 of other distribution type finish heat exchange after enters the mouth on 9.This passage 14 is limiting by sealing strip 4a and sealing lath 4b on the side of its side direction and on distolateral.
Fig. 3 b illustrates the part figure of the cross section of the wide part 2 of undulant fever crossover among Fig. 3 a.The wide part 2 of this type has the height H P of 4mm and the wide part thickness of the type SP of 0.7mm.The wavy extension curve of the wide part 2 of this type repeats within the wavelength LP of 1.6mm.Therefore demarcation strip width B and wavelength LP's is 69 according to ratio of the present invention.
In Fig. 4 with disintegration figure at four passages that do not have to illustrate under the situation of annex air-oil-heat-exchangers of the plate type.
Upwards seal by cover plate 21 by the rectangular parallelepiped 30 that demarcation strip 22 and the wide part 23 or 25 of type constitute.For the size of this rectangular parallelepiped 30 and cover plate 21 and demarcation strip 22 and for the description of its material in this correspondingly suitable Fig. 1 and 2.Uppermost passage 27 is designed to the air of percolation, is positioned at the oil that passage 28 under it is designed to percolation.Be again the passage that is designed to the air of percolation in its lower section, the rest may be inferred.In this heat-exchangers of the plate type, air is directed transverse to the longitudinal direction of rectangular parallelepiped 30 and oil is directed along the longitudinal direction of this rectangular parallelepiped 30.The type exterior feature that the sealing lath 24 of the passage 27 of guiding air has capitalization " E " shape, wherein, the inside of this heat-exchangers of the plate type is pointed at the tip of this capitalization " E ".Described distolateral sealing lath 24 has the thickness of 5.5mm along demarcation strip 22.The passage 28 of guiding oil is by sealing strip 26 sealings of side, and these sealing strips have the width of 12mm along demarcation strip 22.It is different with the wide part 25 of type in the passage 28 that guides oil that the wide part 23 of type in the passage 27 of guiding air is designed to be.In the passage 27 of described guiding air, the wide part 23 of type has the height of 6mm, and these structures repeat with the wavelength of 3.5mm and the wide part of this type has the thickness of 0.7mm.In the passage 28 of described guiding oil, to be 3.5mm and these structures repeat with the wavelength of 1.5mm the wide part height of type.In the passage 28 of guiding oil, the wide part thickness of type also is 0.7mm.In another configuration of the present invention, in the passage of guiding oil, the wide part height of type is 5mm, and the wide part thickness of type is 0.5mm.
The heat-exchangers of the plate type of describing according to above accompanying drawing moves like this, and promptly fluid pressure in the heat-exchangers of the plate type and temperature are no more than 80bar and 70 ℃.In addition, fluid is infeeded like this in these heat-exchangerss of the plate type, i.e. pressure oscillation keeps being 10 liters/minute less than the volume flow in 50% and each passage of design pressure during heat exchange.
Even when not carrying out heat exchange between oil and air, this heat-exchangers of the plate type is also continued percolation by oil, but the volume flow reduction is 0.5 liter/minute.This is in order to make this heat-exchangers of the plate type keep the temperature that improves.
(not shown) for the 3rd embodiment adopts the characteristic of the heat-exchangers of the plate type among Fig. 1 and 2 to a great extent.Being with the difference of first embodiment, only is the thickness that nethermost two demarcation strips and uppermost two demarcation strips have 1.1mm.Inner demarcation strip only has the thickness of 0.8mm.In addition, only be that the wide part of uppermost and nethermost type has the value that provides among Fig. 3 b.Be positioned at inner type exterior feature and have bigger height, the less wide thickness of type and the bigger wide structure wavelength of type.In this configuration of the present invention, in the passage of guiding oil, the wide part height of type is 5mm, and the wide part thickness of type is 0.5mm.In this configuration, wavelength LP is 2.5mm, and the demarcation strip width B is 11cm.
The reference number table
1 demarcation strip
The wide part of 2 heat exchange types
3 distribute the wide part of type
The 4a sealing strip
4b seals lath
5 cover plates
6, the 6a box
7 take over
8 rectangular parallelepiped
9 distribute the wide part inlet of type
14 passages
21 cover plates
22 demarcation strips
The wide part of 23,25 types
24 sealing laths
26 sealing strips
The passage of 27 guiding air
The passage of 28 guiding oil
30 rectangular parallelepiped
The wide part thickness of SP type
The LP wavelength
The HP channel height
B rectangular parallelepiped width
H rectangular parallelepiped height
L rectangular parallelepiped length
Claims (8)
1. heat-exchangers of the plate type, be used for the indirect heat exchange between at least two media liquid and/or gaseous state, this heat-exchangers of the plate type has the matrix of rectangular parallelepiped shape (8) basically, be used to infeed and discharge the device (collector 6 of described medium, 6a, 7) and a plurality ofly stack the passage (14) that shape is arranged basically, these passages are used for making respectively between the medium that adjacent passage (14) flows and carry out indirect heat exchange, wherein, these passages are by the demarcation strip (1 of the distance that separates each other, 22) form, wherein, these demarcation strips are by sealing lath (4a, 4b) the distance that separates each other, these passages have the wide part (fin of wavy type, 2), the wide part of described wavy type is at its crest and trough place and demarcation strip (1,22) form the heat conduction contact, and this stacks by cover plate (5,21) sealing, it is characterized in that, the repeat distance of the width of demarcation strip (B) and the same characteristic features of the wide part of described wavy type (2), for example (wavelength, LP) ratio between has the value in the scope between 15 and 80 to the repeat distance between two crests.
2. heat-exchangers of the plate type according to claim 1 is characterized in that: the ratio between width of demarcation strip (B) and the wavelength (LP) has between 20 and 60, the value in the scope between preferred 28 and 50, between preferred especially 29 and 43.
3. heat-exchangers of the plate type according to claim 1 and 2 is characterized in that: the ratio between width of demarcation strip (B) and the thickness is less than 150.
4. according to each described heat-exchangers of the plate type in the claim 1 to 3, it is characterized in that: the ratio between width of demarcation strip (B) and the thickness has between 50 and 150, the value in the scope between preferred 75 and 115, between preferred especially 80 and 105.
5. according to each described heat-exchangers of the plate type in the claim 1 to 4, it is characterized in that: when the oil that is used as medium at passage (14) flows through, (fin thickness, ratio SP) have the interior value of scope between 7 and 80 to the material thickness of the difference in height between the minimum point of the peak of a crest and a trough (HP) (fin height) and the wide part of described wavy type (2).
6. according to each described heat-exchangers of the plate type in the claim 1 to 5, it is characterized in that: when the oil that is used as medium at passage (14) flow through, the ratio between fin height (HP) and the fin thickness (SP) had between 8 and 20, the value in the scope between preferred 10 and 15.
7. heat-exchangers of the plate type, be used for the indirect heat exchange between at least two media liquid and/or gaseous state, this heat-exchangers of the plate type has the matrix of rectangular parallelepiped shape (8) basically, be used to infeed and discharge the device (collector of described medium, 6,6a, 7) and a plurality ofly stack the passage (14) that shape is arranged basically, these passages are used for making respectively between the medium that adjacent passage (14) flows and carry out indirect heat exchange, and wherein, these passages (14) are by the demarcation strip (1 of the distance that separates each other, 22) form, wherein, these demarcation strips (1,22) are by sealing lath (4a, 4b) the distance that separates each other, and this stacks by cover plate (5,21) sealing, it is characterized in that, described sealing lath (4a, 4b) have a bottom surface and three fins perpendicular to this bottom surface, wherein, these three fins are orientated in this wise, make these fins point to the inside of the matrix of described rectangular parallelepiped shape, and the intermediate fins of these three fins is longer than two outside fins.
In the claim 1 to 7 each described heat-exchangers of the plate type as the application of oil cooler or aerial cooler.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008033302A DE102008033302A1 (en) | 2008-07-15 | 2008-07-15 | Fatigue resistant plate heat exchanger |
| DE102008033302.6 | 2008-07-15 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101629792A true CN101629792A (en) | 2010-01-20 |
Family
ID=41427152
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910151674A Pending CN101629792A (en) | 2008-07-15 | 2009-07-15 | Fatigue-proof plate heat exchanger |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20100025026A1 (en) |
| CN (1) | CN101629792A (en) |
| DE (1) | DE102008033302A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103759474A (en) * | 2014-01-28 | 2014-04-30 | 丹佛斯微通道换热器（嘉兴）有限公司 | Plate heat exchanger |
| CN104215111A (en) * | 2013-05-28 | 2014-12-17 | 哈米尔顿森德斯特兰德公司 | Core assembly for a heat exchanger and method of assembling |
| CN111065879A (en) * | 2017-08-04 | 2020-04-24 | 乔治洛德方法研究和开发液化空气有限公司 | Heat exchanger comprising a multichannel distribution element |
| CN112088285A (en) * | 2018-04-27 | 2020-12-15 | 林德有限责任公司 | Plate heat exchanger, process engineering system and method |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9804607B1 (en) * | 2011-11-16 | 2017-10-31 | Zane Coleman | Fluid transfer systems, devices, components, and methods of manufacture |
| JP6333973B2 (en) * | 2013-10-14 | 2018-05-30 | アイレック アーベー | Heat exchanger plate and heat exchanger |
| US10907500B2 (en) * | 2015-02-06 | 2021-02-02 | Raytheon Technologies Corporation | Heat exchanger system with spatially varied additively manufactured heat transfer surfaces |
| US20170089643A1 (en) * | 2015-09-25 | 2017-03-30 | Westinghouse Electric Company, Llc. | Heat Exchanger |
| EP3150952A1 (en) * | 2015-10-02 | 2017-04-05 | Alfa Laval Corporate AB | Heat transfer plate and plate heat exchanger |
| RU2721950C2 (en) * | 2015-10-06 | 2020-05-25 | Линде Акциенгезельшафт | End plates with surface structure for plate heat exchangers |
| FR3088996B1 (en) * | 2018-11-26 | 2020-12-25 | Air Liquide | A method of manufacturing an exchanger comprising an area to be supported and an exchanger manufactured by such a process |
| EP4343252A1 (en) * | 2022-09-20 | 2024-03-27 | Alfa Laval Corporate AB | A plate heat exchanger |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3847211A (en) * | 1969-01-28 | 1974-11-12 | Sub Marine Syst Inc | Property interchange system for fluids |
| US4623019A (en) * | 1985-09-30 | 1986-11-18 | United Aircraft Products, Inc. | Heat exchanger with heat transfer control |
| US5054545A (en) * | 1990-12-04 | 1991-10-08 | Northern Telecom Limited | Heat exchanger for a sealed cabinet |
| FR2789165B1 (en) * | 1999-02-01 | 2001-03-09 | Air Liquide | HEAT EXCHANGER, PARTICULARLY PLATE HEAT EXCHANGER OF AN AIR SEPARATION APPARATUS |
-
2008
- 2008-07-15 DE DE102008033302A patent/DE102008033302A1/en not_active Withdrawn
-
2009
- 2009-07-15 CN CN200910151674A patent/CN101629792A/en active Pending
- 2009-07-15 US US12/503,520 patent/US20100025026A1/en not_active Abandoned
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104215111A (en) * | 2013-05-28 | 2014-12-17 | 哈米尔顿森德斯特兰德公司 | Core assembly for a heat exchanger and method of assembling |
| CN103759474A (en) * | 2014-01-28 | 2014-04-30 | 丹佛斯微通道换热器（嘉兴）有限公司 | Plate heat exchanger |
| WO2015113496A1 (en) * | 2014-01-28 | 2015-08-06 | 丹佛斯微通道换热器（嘉兴）有限公司 | Board-type heat exchanger |
| CN103759474B (en) * | 2014-01-28 | 2018-01-02 | 丹佛斯微通道换热器（嘉兴）有限公司 | Plate type heat exchanger |
| CN111065879A (en) * | 2017-08-04 | 2020-04-24 | 乔治洛德方法研究和开发液化空气有限公司 | Heat exchanger comprising a multichannel distribution element |
| CN111065879B (en) * | 2017-08-04 | 2021-08-24 | 乔治洛德方法研究和开发液化空气有限公司 | Heat exchanger comprising a multichannel distribution element |
| CN112088285A (en) * | 2018-04-27 | 2020-12-15 | 林德有限责任公司 | Plate heat exchanger, process engineering system and method |
Also Published As
| Publication number | Publication date |
|---|---|
| US20100025026A1 (en) | 2010-02-04 |
| DE102008033302A1 (en) | 2010-01-21 |
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Application publication date: 20100120 |