US3570593A - Heat-exchanger - Google Patents

Heat-exchanger Download PDF

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Publication number
US3570593A
US3570593A US791691*A US3570593DA US3570593A US 3570593 A US3570593 A US 3570593A US 3570593D A US3570593D A US 3570593DA US 3570593 A US3570593 A US 3570593A
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US
United States
Prior art keywords
shapes
passages
pipes
exchanger
parallel
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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.)
Expired - Lifetime
Application number
US791691*A
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English (en)
Inventor
Raymond Isaaz
Georges Vailhen
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SOC TRANE
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SOC TRANE
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M3/00—Investigating fluid-tightness of structures
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0041—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having parts touching each other or tubes assembled in panel form
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
    • F28F7/02—Blocks traversed by passages for heat-exchange media
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M3/00—Investigating fluid-tightness of structures
    • G01M3/02—Investigating fluid-tightness of structures by using fluid or vacuum
    • G01M3/26—Investigating fluid-tightness of structures by using fluid or vacuum by measuring rate of loss or gain of fluid, e.g. by pressure-responsive devices, by flow detectors
    • G01M3/32—Investigating fluid-tightness of structures by using fluid or vacuum by measuring rate of loss or gain of fluid, e.g. by pressure-responsive devices, by flow detectors for containers, e.g. radiators
    • G01M3/3227—Investigating fluid-tightness of structures by using fluid or vacuum by measuring rate of loss or gain of fluid, e.g. by pressure-responsive devices, by flow detectors for containers, e.g. radiators for radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/16—Safety or protection arrangements; Arrangements for preventing malfunction for preventing leakage

Definitions

  • the present invention is relating to a heat-exchanger of the type comprising a plurality of parallel passages, each of them containing a packing made in particular of a corrugated sheet.
  • Such exchangers often called compact exchangers, are known wherein said passages are limited by parallel separating plates and wherein the successive passages are alternatively connected to two circuits conducting two exchange fluids, respectively.
  • the various passages are assembled by brazing the packings on the adjacent separating plates.
  • the packing is, for example, a periodically deformed sheet alternatively into contact with each of the two separating plates adjacent the corresponding passage, said sheet being brazed on said plates at the level of the points of contact.
  • the invention aims essentially at keeping the advantages of said kind of exchangers, particularly their compactness and the very good efficiency of the exchange, while allowing to increase the safety in operation if they are designed for an exchange between two fluids that have to be prevented from being into contact, for example if said fluids can give rise to a really dangerous reaction if they are brought in presence of one another.
  • the invention aims at increasing the importance of the number of the barriers separating the circuits of the two fluids without affecting the exchange, or, for the least, at more easily detecting the possible leakages from one or the other of the circuits.
  • the invention relates to an exchanger comprising a plurality of parallel passages for a first fluid, each of said passages containing a packing made in particular of a corrugated sheet, said exchanger being essentially characterized in that it comprises, in alternation with said passages, groups of parallel shapes, each of said shapes being provided with a longitudinal channel for the circulation of a second fluid and having two opposed faces respectively adjacent to the two successive passages disposed on each side of the corresponding group of shapes, the shapes of a same group limiting between them collecting spaces for detecting the possible leakages.
  • the exchanger according to the invention is particularly convenient if the first fluid is a gaseous one and the second fluid, a liquid one. As a matter of fact, it allows to adapt at best the relation between the exchange surfaces respectively in contact with each of the two fluids, with respect to the relative exchange factors of said fluids.
  • every passage for the first fluid is limited by two parallel plates, both in thermal contact with the packing of the passage and the adjacent shapes.
  • the shapes contain pipes within the channels for the circulation of the second fluid.
  • the exchanger according to the invention comprises, preferably but not necessarily, both such plates and such pipes that form two additional barriers, added to the barrier formed by the shapes, between the circuits of the two fluids materialized the one, by the passages between the plates, the other, by the pipes within the shapes. Said barriers prevent any contact between the two fluids with a practically total safety.
  • the shapes, the packings and the separating plates, occasionally mounted, limiting the passages for the first fluid aremade of aluminum and interconnected by brazing them with a silicon-aluminium alloy, for example. While ensuring the cohesion of the assembly, the brazed connections make for the heat conduction between the various elements.
  • Pipes made of a material different from the one of the shape can be disposed within said shapes.
  • the connection between the pipes and the shapes can be made by expanding the pipes for example.
  • the use of said pipes allows to choose the materi' als with respect of the particular properties of every fluid.
  • the shapes are made of aluminum the pipes can be made of any other metal or alloy so that said pipes can conduct a second fluid liable to attack aluminum.
  • the heat-exchanger is more particularly designed for a heat exchange between a first gaseous fluid and a second liquid fluid, said fluids being liable to react dangerously one with another: for example uranium hexafluoride and water.
  • the exchanger according to the invention can be used advantageously for other applications, for example in cryogeny, if one of the exchange fluids is used under a high pressure.
  • FIG. I is an exploded view of a first embodiment of the exchanger according to the invention wherein said exchanger has a parallelepipedic shape;
  • FIG. 2 shows another embodiment wherein the exchanger is limited by a cylindrical volume
  • FIG. 3 is another embodiment of the exchanger shown in the FIG. 1, wherein the plane plates limiting the passages for the first exchange fluid are suppressed;
  • FIG. 4 shows other embodiments for the passages of the first fluid, for the shapes and for the conducting pipes of the second fluid
  • FIGS. 5 and 6 are schematic views, given by way of example, of two embodiments relating to the distribution of the second exchange fluid in the pipes of the exchanger shown in the FIG. 1.
  • the exchanger shown in the FIG. 1 is essentially made of a stacking of a member of passages 1 having a rectangular section, limited by plane plates 2, 3 that separate them from groups of shapes 4 mounted in alternation with said passages.
  • the various passages such as 1 form together a circuit A conducting the first exchange fluid in operation, said first exchange fluid being a gas in the described particular case.
  • the shapes 4, which have a square or rectangular external section they are each provided with a longitudinal channel 5 in which is mounted a pipe 6, and the pipes 6 form a circuit B conducting the second exchange fluid in operation, said second exchange fluid being a liquid such as water in the inpoint case.
  • the exchanger of the FIG. 1 having a general parallelepipedic shape, the pipes of the circuit B are mounted in it in a direction perpendicular to the direction of the circulation of the gas through the circuit A (passage 1) so that the circulation 66 of the two fluids is of the crossflow type, at least locally.
  • the various passages of the circuit A are fed in parallel from one face of the exchanger, through a conduit B opening in a distributing dome 9. On the opposed face, the gas emerging from the various passages'is collected in a similar dome, not shown.
  • a sheet 12 is mounted that describes regular corrugations between the two separating plates limiting said passage. Said sheet is also brazed on the separating plates; it acts as a spacing element between the two plates while forming a secondary exchange surface ensuring the conduction of the calories of the gas towards the separating plates and, subsequently, towards the circuit B.
  • corrugated sheets must have various shapes; the corrugations can be rounded or rectangular; they can be provided in rectangular pattern or in herring bone pattern; the sheets can be eventually apertured.
  • the various pipes passing through the shapes 4 of a same group are connected by means of bent parts 14 mounted in succession at each of their extremities, or by means of removable collectors allowing the access to the pipes for cleaning them.
  • the liquid circulates in series through the various pipes of a same group of shapes.
  • the successive groups are fed in parallel from a common collector 15.
  • a similar collector on the opposed face of the exchanger, collects the liquid emerging from the last pipe of every group of shapes. If the number of going up and going down nappes of pipes 6 is sufficient from one collector to the other, the circulation can be regarded as a circulation of the countercurrent type.
  • the adjacent shapes of a same group are slightly spaced one from the other so that they limit between them parallel spaces 16 destined to collect the possible escaped fluid and to allow the detection of such leakages. Said spaces are preferably connected to an escape collecting circuit.
  • the elements of the circuit A bars 10, separating plates 2, 3 and corrugated sheets 12, are made of aluminum as the shapes 4. Said various elements are brazed in a salt bath.
  • the pipes of the circuit B are expanded on their whole length within the shapes. They are made of a cupreous alloy or of any other metal chosen with respect of the nature of the driven liquid.
  • the described exchanger presents therefore the advantages of the exchangers of the compact type made of brazed aluminum while allowing to use an exchange fluid incompatible with aluminum.
  • corrugated sheets form an additional and secondary exchange surface that increases in great proportions the total exchange factor.
  • Said secondary surface has the advantage of being easily adapted for every particular application, independently of the pipes of the circuit B, in function of the exchange conditions to be taken into account flow rates, temperatures, exchange factors and pressure-drops, particularly.
  • An essential advantage of the described embodiment is moreover the safety in the case in which any contact between the two fluids is dangerous. Said safety is insured by the presence of several barriers separating the two fluids one from the other. Said barriers are indeed provided at every level: the pipe of the circuit B, the shape and the plate limiting the passage of the circuit A. In order that the fluids can come into contact, it would be necessary that a leakage could occur simultaneously and at the same place through the three barriers, that is practically impossible.
  • the described exchanger has also other advantages due in particular to the divided shape of the two circuits and to the use of brazed metal.
  • the divided shape of the circuit A which comprises a great number of elementary passages heated or cooled on each of their sides by two parts of the circuit B, increases the exchange performances due to the large surface of the corrugated sheets.
  • brazed aluminum leads to a particularly compact and resisting structure and allows to prevent the strains in assembling the elements of the exchanger.
  • the small sizes and weight of the exchanger allow to treat very important flow rates in a relatively small exchange volume.
  • the described exchanger is economically and reliably manufactured owing to its simple design.
  • the design of the exchanger according to the invention allows also to easily adapt it to any particular shape of the volume available for it. Such a possibility is illustrated by the embodiment shown in the FIG. 2.
  • the exchanger is limited by a cylindrical volume.
  • said exchanger is provided with passages 18 for the circuit of the gas, each of them containing a corrugated sheet, and with shapes 119, each of them containing a pipe 20 for the circuit of the liquid and being separated from the passages 18 by parallel plates 21.
  • said plates are curved for giving them a cylindrical shape, the passages 18 being, in said case, sectors of annular crowns.
  • the circulation of the two fluids is of the crossflow type, the shapes 19 being in parallel with the axis of the exchanger.
  • the pipes 20 are connected to collectors not shown.
  • the gas enters the passages 18 and emerges from them through two distributing boxes 22 and 23, respectively, that are diametrally opposed in the cylindri cal exchanger.
  • the pipes provided in the above described embodiments can be suppressed, the liquid circulating therefore directly through the channels provided in the shapes.
  • the shapes are provided on their face into contact with the separating plates, with grooves 26 that make for an easier detection of the possible leakages at said level either through the separating plate or through the shape.
  • the pipes of the circuit B can have, on the other hand, any particular shape adapted to the fluid circulated and to the exchange conditions.
  • they can contain star pattern devices 27 allowing to increase the exchange surface into contact with the liquid.
  • They can also be provided with external grooves allowing to rapidly detect any leakage through the pipe itself, and thus to prevent the risks of corrosion of the shape; in this case, it is advantageous to mount the pipes by forcing them into the shapes, without expanding them.
  • the grooves can be provided, not on thepipes, but on the shapes as shown in the FIG. 3 by the shape 30.
  • the pipes can be provided with inner spiral shaped or spring shaped disturbers.
  • FIG. 4 shows, by way of example, that the passages can be constituted with two corrugated sheets separated by an intermediate plate 28.
  • one embodiment of the exchanger may operate by establishing the circuit B in different manner.
  • the pipes of a same group of shapes are connected in series and the various groups are fed in parallel
  • a heat exchanger comprising a plurality of parallel passages for a gas, parallel plates forming said passages, a packing of corrugated sheet in each of said passages, and, stacked in alternation with each of said passages, groups of parallel interengaging shapes, each of said shapes having a longitudinal channel for the circulation of a liquid, two opposed faces for each of said shapes respectively adjacent to liquid to and removing liquid from said pipes.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US791691*A 1968-02-05 1969-01-16 Heat-exchanger Expired - Lifetime US3570593A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR138754 1968-02-05

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BE (1) BE727458A (es)
FR (1) FR1580856A (es)
GB (1) GB1227221A (es)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5000253A (en) * 1988-03-31 1991-03-19 Roy Komarnicki Ventilating heat recovery system
WO1997003281A1 (en) * 1995-07-10 1997-01-30 Westinghouse Electric Corporation Preheating of gas turbine fuel with compressed cooling air
US6070672A (en) * 1998-01-20 2000-06-06 Halliburton Energy Services, Inc. Apparatus and method for downhole tool actuation
EP1998131A1 (en) * 2007-05-29 2008-12-03 Sanden Corporation Gas cooler for hot-water supply system
US20090294110A1 (en) * 2008-05-30 2009-12-03 Foust Harry D Spaced plate heat exchanger
US20100051246A1 (en) * 2006-12-08 2010-03-04 Korea Atomic Energy Research Institute High temperature and high pressure corrosion resistant process heat exchanger for a nuclear hydrogen production system
US20100263823A1 (en) * 2009-04-20 2010-10-21 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel Ltd) Plate fin heat exchanger
CN102538518A (zh) * 2012-02-15 2012-07-04 国电联合动力技术有限公司 一种板翅式空冷换热器
EP2244045A3 (de) * 2009-04-21 2013-03-27 Linde Aktiengesellschaft Plattenwärmeaustauscher mit Profilen
FR2981123A1 (fr) * 2011-10-07 2013-04-12 Snecma Dispositif de refroidissement d'air dans un moteur d'aeronef
EP2706318A1 (en) * 2011-05-06 2014-03-12 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle device provided with same
US20140318125A1 (en) * 2011-12-13 2014-10-30 Kroens Co., Ltd. Apparatus for generating superheated vapor using waste heat recovery
US20160161189A1 (en) * 2014-12-04 2016-06-09 Honeywell International Inc. Plate-fin tubular hybrid heat exchanger design for an air and fuel cooled air cooler
CN106716046A (zh) * 2014-07-25 2017-05-24 集成测试与测量公司 用于使用振动分析来检测、监测和移除锅炉热交换器表面上的沉积物的系统和方法
US20190204012A1 (en) * 2018-01-04 2019-07-04 Hamilton Sundstrand Corporation Curved heat exchanger
WO2021024176A1 (en) * 2019-08-07 2021-02-11 Ibj Technology Ivs Cost effective heat exchangers for thermochemical biomass conversion.

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8003708U1 (de) * 1980-02-12 1980-08-28 Isartaler Schraubenkompressoren Gmbh, 8192 Gertsried Kondensatabscheider fuer einen kuehler
DE3501936A1 (de) * 1985-01-22 1986-07-24 Dieter Steinegg-Appenzell Steeb Kreuzstrom-waermetauscher mit mindestens zwei plattenpaketen

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1916395A (en) * 1931-01-14 1933-07-04 Alfred L Stamsvik Heat exchange apparatus
US2606007A (en) * 1947-10-16 1952-08-05 Modine Mfg Co Heat exchanger
US2985434A (en) * 1957-03-15 1961-05-23 Air Preheater Regenerator
US3225824A (en) * 1962-09-29 1965-12-28 Wartenburg Kurt Air-cooled heat exchanger for cooling liquid media
US3267564A (en) * 1964-04-23 1966-08-23 Calumet & Hecla Method of producing duplex internally finned tube unit
US3451473A (en) * 1967-04-11 1969-06-24 United Aircraft Corp Heat exchanger construction

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1916395A (en) * 1931-01-14 1933-07-04 Alfred L Stamsvik Heat exchange apparatus
US2606007A (en) * 1947-10-16 1952-08-05 Modine Mfg Co Heat exchanger
US2985434A (en) * 1957-03-15 1961-05-23 Air Preheater Regenerator
US3225824A (en) * 1962-09-29 1965-12-28 Wartenburg Kurt Air-cooled heat exchanger for cooling liquid media
US3267564A (en) * 1964-04-23 1966-08-23 Calumet & Hecla Method of producing duplex internally finned tube unit
US3451473A (en) * 1967-04-11 1969-06-24 United Aircraft Corp Heat exchanger construction

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5000253A (en) * 1988-03-31 1991-03-19 Roy Komarnicki Ventilating heat recovery system
WO1997003281A1 (en) * 1995-07-10 1997-01-30 Westinghouse Electric Corporation Preheating of gas turbine fuel with compressed cooling air
US6070672A (en) * 1998-01-20 2000-06-06 Halliburton Energy Services, Inc. Apparatus and method for downhole tool actuation
US20100051246A1 (en) * 2006-12-08 2010-03-04 Korea Atomic Energy Research Institute High temperature and high pressure corrosion resistant process heat exchanger for a nuclear hydrogen production system
US8381803B2 (en) * 2006-12-08 2013-02-26 Korea Atomic Energy Research Institute High temperature and high pressure corrosion resistant process heat exchanger for a nuclear hydrogen production system
EP1998131A1 (en) * 2007-05-29 2008-12-03 Sanden Corporation Gas cooler for hot-water supply system
JP2008298311A (ja) * 2007-05-29 2008-12-11 Sanden Corp 給湯システムのガスクーラ
US20090294110A1 (en) * 2008-05-30 2009-12-03 Foust Harry D Spaced plate heat exchanger
US8079508B2 (en) 2008-05-30 2011-12-20 Foust Harry D Spaced plate heat exchanger
US20100263823A1 (en) * 2009-04-20 2010-10-21 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel Ltd) Plate fin heat exchanger
US8985192B2 (en) * 2009-04-20 2015-03-24 Kobe Steel, Ltd. Plate fin heat exchanger
EP2244045A3 (de) * 2009-04-21 2013-03-27 Linde Aktiengesellschaft Plattenwärmeaustauscher mit Profilen
EP2706318A4 (en) * 2011-05-06 2014-11-19 Mitsubishi Electric Corp HEAT EXCHANGER AND COLD CIRCUIT DEVICE THEREWITH
EP2706318A1 (en) * 2011-05-06 2014-03-12 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle device provided with same
FR2981123A1 (fr) * 2011-10-07 2013-04-12 Snecma Dispositif de refroidissement d'air dans un moteur d'aeronef
US20140318125A1 (en) * 2011-12-13 2014-10-30 Kroens Co., Ltd. Apparatus for generating superheated vapor using waste heat recovery
CN102538518A (zh) * 2012-02-15 2012-07-04 国电联合动力技术有限公司 一种板翅式空冷换热器
CN106716046A (zh) * 2014-07-25 2017-05-24 集成测试与测量公司 用于使用振动分析来检测、监测和移除锅炉热交换器表面上的沉积物的系统和方法
US10094660B2 (en) 2014-07-25 2018-10-09 Integrated Test & Measurement (ITM), LLC System and methods for detecting, monitoring, and removing deposits on boiler heat exchanger surfaces using vibrational analysis
CN106716046B (zh) * 2014-07-25 2019-02-22 集成测试与测量公司 用于使用振动分析来检测、监测和移除锅炉热交换器表面上的沉积物的系统和方法
US10724858B2 (en) 2014-07-25 2020-07-28 Integrated Test & Measurement (ITM), LLC System and methods for detecting, monitoring, and removing deposits on boiler heat exchanger surfaces using vibrational analysis
US20160161189A1 (en) * 2014-12-04 2016-06-09 Honeywell International Inc. Plate-fin tubular hybrid heat exchanger design for an air and fuel cooled air cooler
US9682782B2 (en) * 2014-12-04 2017-06-20 Honeywell International Inc. Plate-fin tubular hybrid heat exchanger design for an air and fuel cooled air cooler
US20190204012A1 (en) * 2018-01-04 2019-07-04 Hamilton Sundstrand Corporation Curved heat exchanger
EP3508805A3 (en) * 2018-01-04 2019-09-25 Hamilton Sundstrand Corporation Curved heat exchanger
US10670346B2 (en) * 2018-01-04 2020-06-02 Hamilton Sundstrand Corporation Curved heat exchanger
WO2021024176A1 (en) * 2019-08-07 2021-02-11 Ibj Technology Ivs Cost effective heat exchangers for thermochemical biomass conversion.

Also Published As

Publication number Publication date
GB1227221A (es) 1971-04-07
BE727458A (es) 1969-07-01
FR1580856A (es) 1969-09-12

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