US20020153129A1 - Integral fin passage heat exchanger - Google Patents
Integral fin passage heat exchanger Download PDFInfo
- Publication number
- US20020153129A1 US20020153129A1 US09/557,347 US55734700A US2002153129A1 US 20020153129 A1 US20020153129 A1 US 20020153129A1 US 55734700 A US55734700 A US 55734700A US 2002153129 A1 US2002153129 A1 US 2002153129A1
- Authority
- US
- United States
- Prior art keywords
- fin
- integral
- plates
- passages
- heat exchanger
- 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.)
- Abandoned
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D9/0081—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 a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/108—Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow
Definitions
- the present invention relates generally to heat exchangers. More specifically, the present invention relates to a plate-fin heat exchanger.
- a typical plate-fin heat exchanger includes a core and manifolds.
- the core includes a plurality of plates, a plurality of fins located between and bonded to the plates, and a plurality of closure bars.
- the plates and fins define hot side and cold side passageways.
- the closure bars provide closure of the fins and precise spacing between the plates.
- a hot fluid flows through the hot side passageways and a cold fluid flows through the cold side passageways. Heat is transferred from the hot fluid to the cold fluid.
- the manifolds direct the hot fluid and cold fluid to and from the hot side and cold side passageways.
- a large number of parts are assembled during construction of the metal core, and great care is taken to assemble the parts.
- a large number of welds and braze joints are made during the construction of the metal core.
- the core of a plate-fin heat exchanger has a reduced parts count.
- the heat exchanger core comprises first and second integral fin passages, each integral fin passage having integrally formed plates and extended surfaces; and a fin located between and bonded to outer surfaces of the first and second integral fin passages. Reducing the parts count simplifies the construction of the core and reduces the number of brazed joints that could possibly leak.
- FIG. 1 is an exploded view of a heat exchanger core according to the present invention
- FIGS. 2 a and 2 b are illustrations of two different fin geometries
- FIG. 3 is an illustration of a header plate and integral fin passages of another heat exchanger core according to the present invention.
- FIG. 4 is a flowchart of a method of constructing a heat exchanger according to the present invention.
- FIGS. 5 a and 5 b are illustrations of different profiles of passageways within the integral fin passages.
- FIG. 1 illustrates a heat exchanger core 10 .
- the core 10 includes a plurality of integral fin passages 12 and a plurality of fins 14 .
- Each integral fin passage 12 includes a pair of plates 16 and a plurality of extended surfaces 18 between the plates 16 .
- the plates 16 and the extended surfaces 18 define straight fluid passageways 20 .
- the two extended surfaces 18 a and 18 b at the edges of the plates 16 also function as closure bars.
- the plates 16 and the extended surfaces 18 are integrally formed. That is, they form a unitary structure.
- the integral fin passages 12 may be formed by extrusion. Any extrudable material having good heat transfer characteristics may be used for the integral fin passages 12 . Such material includes, without limitation, copper and aluminum. Using integral fin passages 12 reduces the parts count of the heat exchanger core 10 .
- Each fin 14 is located between and bonded to outer surfaces of adjacent integral fin passages 12 .
- Each fin 14 may have a metal core 14 a that is clad with a braze material 14 b (a portion of the braze material has been removed to show the metal core 14 a ).
- the braze material 14 b enhances the bond between the fins 14 and the extruded passages 12 .
- the plates 16 and the fins 14 define second fluid passageways 22 .
- the second fluid passageways 22 may provide any type of flow path.
- the second fluid passageways 22 may be straight and arranged to provide a cross-flow relative to the first fluid passageways 20 .
- the core 10 may instead include inlet and outlet turning fins 24 for providing co-current (i.e., same direction) or countercurrent (i.e., opposite direction) flow relative to the first fluid passageways 20 .
- the inlet and outlet turning fins 24 may be oriented to provide generally either a Z-flow path or a U-flow path.
- a Z-flow path begins at one end of the heat exchanger core 10 and ends at an opposite side and opposite corner.
- a U-flow path begins and ends on the same side, but opposite corners of the core 10 .
- the inlet and outlet turning fins 24 may be oriented at various angles relative to the first fluid passageway 20 .
- FIG. 1 happens to show fins 14 providing a Z-flow path, with the turning fins 24 being oriented at a 90 degree angle relative to the first fluid passageway 20 .
- the integral fin passages 12 and fins 14 may be stacked in an alternating sequence (in the z-direction). Thus, each fin 14 is located between a pair of adjacent integral fin passages 12 .
- Individual closure bars 26 may be located at edges of, and brazed between, plates 16 of adjacent integral fin passages 12 .
- Each individual closure bar 26 may be made of a metal core having a braze cladding.
- the closure bars 26 provide closure for the second fluid passageways 22 and they provide precise spacing between the integral fin passages 12 . Closure for the second fluid passageways 22 may be provided by four straight or two L-shaped closure bars. The topmost closure bars 26 have been omitted for clarity.
- closure bars for the sides of the fins 14 may be formed integrally with the plates 16 of the integral fin passage 12 .
- An extruded closure bar of one integral passage would be brazed or welded to an adjacent integral fin passage 12 .
- Forming the fin closure bars as part of the integral fin passages 12 further reduces the parts count of the heat exchanger core 10 .
- the integral fin passages 12 may provide the hot side or cold side passageways.
- a first fluid enters the first end of the integral fin passages 12 , passes straight though the core 10 (in a y-direction) and exits a second end of the integral passages 12 .
- a second fluid enters one corner of the core 10 (in an x-direction), is turned to flow parallel to the first fluid (in the y-direction), and is turned again to flow out of the opposite corner of the core 10 (in the x-direction). Heat is transferred from the hot fluid to the cold fluid.
- Manifolds (not shown) direct the hot fluid and cold fluid to and from the hot side and cold side passageways.
- the fins 14 may have any typical heat transfer fin geometry.
- the fin geometry may be plain rectangular (FIG. 1), rectangular offset (FIG. 2 a ) or wavy (FIG. 2 b ).
- Other types of fin geometries include, without limitation, perforated geometry, plain triangular geometry and louvered geometry.
- the heat exchanger core 10 may provide any type of flow path.
- Types of countercurrent and co-current paths include, without limitation, straight flow paths, ‘Z’-flow paths and ‘U’-flow paths.
- a simple cross flow heat exchanger having an entirely straight rectangular fin geometry may be formed by stacking integral fin passages in a z-direction. Integral fin passages for the hot fluid may extend in the x-direction and integral fin passages for the cold fluid may extend along the y-direction.
- another heat exchanger core 110 includes first and second header plates 126 instead of the individual closure bars.
- the header plates 126 serve the same function as the individual closure bars: providing closure for the fluid flowing between each of the integral fin passages 112 as well as providing precise spacing between the integral fin passages 112 .
- the header plates 126 may be machined or formed from sheet metal.
- a heat exchanger core 110 having two header plates 126 has a lower parts count than a core 10 having multiple closure bars 26 .
- the integral fin passages 112 may be brazed or welded to the header plates 126 .
- a method of fabricating a heat exchanger core includes the following steps.
- a plurality of integral fin passages are provided, with each integral fin passage having been extruded to form plates and extended surfaces (block 202 ).
- Fins and closure structures e.g., closure bars, header plates
- the fins and closure structures are brazed or otherwise bonded to the integral fin passages (block 206 ).
- the integral fin passages, the fins and the closure structures are brazed together at the same time.
- manifolds are welded or otherwise mounted to the closure bars of the heat exchanger core (block 208 ).
- the manifolds may also be clad with a braze material.
- the integral fin passages are not limited to passageways having rectangular profiles.
- the passageways may have round or other profiles. See, for example, FIGS. 5 a and 5 b.
- integral fin passages are not limited to the design shown in the drawings.
- an alternative integral fin passageway could include a flattened tube and a fin within the flattened tube.
- Such an alternative integral fin passage would have plates and closure bars that are integrally formed.
Abstract
A plate-fin heat exchanger includes a plurality of integral fin passages and a plurality of fins. Each fin is located between and bonded to outer surfaces of adjacent integral fin passages. Each integral fin passage has integrally formed plates and extended surfaces. The integral fin passages may be formed by extrusion.
Description
- The present invention relates generally to heat exchangers. More specifically, the present invention relates to a plate-fin heat exchanger.
- A typical plate-fin heat exchanger includes a core and manifolds. The core includes a plurality of plates, a plurality of fins located between and bonded to the plates, and a plurality of closure bars. The plates and fins define hot side and cold side passageways. The closure bars provide closure of the fins and precise spacing between the plates. During operation of the heat exchanger, a hot fluid flows through the hot side passageways and a cold fluid flows through the cold side passageways. Heat is transferred from the hot fluid to the cold fluid. The manifolds direct the hot fluid and cold fluid to and from the hot side and cold side passageways.
- A large number of parts are assembled during construction of the metal core, and great care is taken to assemble the parts. A large number of welds and braze joints are made during the construction of the metal core.
- Reducing the number of parts would simplify the construction of the metal core and reduce the cost of construction. Reducing the number of parts would also reduce the number of brazed joints that could possibly leak.
- Therefore, it is desirable to reduce the parts count of plate-fin heat exchangers.
- The core of a plate-fin heat exchanger according to the present invention has a reduced parts count. The heat exchanger core comprises first and second integral fin passages, each integral fin passage having integrally formed plates and extended surfaces; and a fin located between and bonded to outer surfaces of the first and second integral fin passages. Reducing the parts count simplifies the construction of the core and reduces the number of brazed joints that could possibly leak.
- FIG. 1 is an exploded view of a heat exchanger core according to the present invention;
- FIGS. 2a and 2 b are illustrations of two different fin geometries;
- FIG. 3 is an illustration of a header plate and integral fin passages of another heat exchanger core according to the present invention;
- FIG. 4 is a flowchart of a method of constructing a heat exchanger according to the present invention; and
- FIGS. 5a and 5 b are illustrations of different profiles of passageways within the integral fin passages.
- Reference is made to FIG. 1, which illustrates a heat exchanger core10. The core 10 includes a plurality of
integral fin passages 12 and a plurality offins 14. Eachintegral fin passage 12 includes a pair ofplates 16 and a plurality ofextended surfaces 18 between theplates 16. Theplates 16 and theextended surfaces 18 definestraight fluid passageways 20. The twoextended surfaces plates 16 also function as closure bars. - The
plates 16 and theextended surfaces 18 are integrally formed. That is, they form a unitary structure. For instance, theintegral fin passages 12 may be formed by extrusion. Any extrudable material having good heat transfer characteristics may be used for theintegral fin passages 12. Such material includes, without limitation, copper and aluminum. Usingintegral fin passages 12 reduces the parts count of the heat exchanger core 10. - Each
fin 14 is located between and bonded to outer surfaces of adjacentintegral fin passages 12. Eachfin 14 may have ametal core 14 a that is clad with abraze material 14 b (a portion of the braze material has been removed to show themetal core 14 a). Thebraze material 14 b enhances the bond between thefins 14 and theextruded passages 12. - The
plates 16 and thefins 14 definesecond fluid passageways 22. Thesecond fluid passageways 22 may provide any type of flow path. For example, thesecond fluid passageways 22 may be straight and arranged to provide a cross-flow relative to thefirst fluid passageways 20. The core 10 may instead include inlet and outlet turning fins 24 for providing co-current (i.e., same direction) or countercurrent (i.e., opposite direction) flow relative to thefirst fluid passageways 20. The inlet and outlet turning fins 24 may be oriented to provide generally either a Z-flow path or a U-flow path. A Z-flow path begins at one end of the heat exchanger core 10 and ends at an opposite side and opposite corner. A U-flow path begins and ends on the same side, but opposite corners of the core 10. The inlet and outlet turning fins 24 may be oriented at various angles relative to thefirst fluid passageway 20. FIG. 1 happens to showfins 14 providing a Z-flow path, with the turningfins 24 being oriented at a 90 degree angle relative to thefirst fluid passageway 20. - The
integral fin passages 12 andfins 14 may be stacked in an alternating sequence (in the z-direction). Thus, eachfin 14 is located between a pair of adjacentintegral fin passages 12. -
Individual closure bars 26 may be located at edges of, and brazed between,plates 16 of adjacentintegral fin passages 12. Eachindividual closure bar 26 may be made of a metal core having a braze cladding. Theclosure bars 26 provide closure for thesecond fluid passageways 22 and they provide precise spacing between theintegral fin passages 12. Closure for thesecond fluid passageways 22 may be provided by four straight or two L-shaped closure bars. Thetopmost closure bars 26 have been omitted for clarity. - Instead of using
individual closure bars 26, closure bars for the sides of the fins 14 (in the direction of the first fluid passageways 20) may be formed integrally with theplates 16 of theintegral fin passage 12. An extruded closure bar of one integral passage would be brazed or welded to an adjacentintegral fin passage 12. Forming the fin closure bars as part of theintegral fin passages 12 further reduces the parts count of the heat exchanger core 10. - The
integral fin passages 12 may provide the hot side or cold side passageways. During operation of the heat exchanger shown in FIG. 1, a first fluid enters the first end of theintegral fin passages 12, passes straight though the core 10 (in a y-direction) and exits a second end of theintegral passages 12. A second fluid enters one corner of the core 10 (in an x-direction), is turned to flow parallel to the first fluid (in the y-direction), and is turned again to flow out of the opposite corner of the core 10 (in the x-direction). Heat is transferred from the hot fluid to the cold fluid. Manifolds (not shown) direct the hot fluid and cold fluid to and from the hot side and cold side passageways. - The
fins 14 may have any typical heat transfer fin geometry. For example, the fin geometry may be plain rectangular (FIG. 1), rectangular offset (FIG. 2a) or wavy (FIG. 2b). Other types of fin geometries include, without limitation, perforated geometry, plain triangular geometry and louvered geometry. - The heat exchanger core10 may provide any type of flow path. Types of countercurrent and co-current paths include, without limitation, straight flow paths, ‘Z’-flow paths and ‘U’-flow paths.
- A simple cross flow heat exchanger having an entirely straight rectangular fin geometry may be formed by stacking integral fin passages in a z-direction. Integral fin passages for the hot fluid may extend in the x-direction and integral fin passages for the cold fluid may extend along the y-direction.
- Referring now to FIG. 3, another
heat exchanger core 110 includes first andsecond header plates 126 instead of the individual closure bars. Theheader plates 126 serve the same function as the individual closure bars: providing closure for the fluid flowing between each of theintegral fin passages 112 as well as providing precise spacing between theintegral fin passages 112. Theheader plates 126 may be machined or formed from sheet metal. Aheat exchanger core 110 having twoheader plates 126 has a lower parts count than a core 10 having multiple closure bars 26. Theintegral fin passages 112 may be brazed or welded to theheader plates 126. - Reference is now made to FIG. 4. A method of fabricating a heat exchanger core includes the following steps. A plurality of integral fin passages are provided, with each integral fin passage having been extruded to form plates and extended surfaces (block202). Fins and closure structures (e.g., closure bars, header plates) are assembled with the integral fin passages (block 204). The fins and closure structures are brazed or otherwise bonded to the integral fin passages (block 206). Thus, the integral fin passages, the fins and the closure structures are brazed together at the same time. After the core has been brazed, manifolds are welded or otherwise mounted to the closure bars of the heat exchanger core (block 208). The manifolds may also be clad with a braze material.
- The integral fin passages are not limited to passageways having rectangular profiles. The passageways may have round or other profiles. See, for example, FIGS. 5a and 5 b.
- The integral fin passages are not limited to the design shown in the drawings. For instance, an alternative integral fin passageway could include a flattened tube and a fin within the flattened tube. Such an alternative integral fin passage would have plates and closure bars that are integrally formed.
- The present invention is not limited to the specific embodiments described above. Instead, the present invention is construed according to the claims that follow.
Claims (20)
1. A heat exchanger comprising:
first and second integral fin passages, each integral fin passage having integrally formed plates and extended surfaces; and
a fin located between and bonded to outer surfaces of the first and second integral fin passages.
2. The heat exchanger of claim 1 , wherein extended surfaces at edges of the plates provide closure bars for the integral fin passages.
3. The heat exchanger of claim 2 , wherein at least one integral fin passage further includes a closure bar for the fin.
4. The heat exchanger of claim 2 , further comprising closure bars for the fin, each closure bar being located between and bonded to the outer surfaces of the first and second integral fin passages.
5. The heat exchanger of claim 1 , further comprising first and second header plates, first ends of the integral fin passages fitting into slots in the first header plate, second ends of the integral fin passages fitting into slots in the second header plate, the header plates providing closure for the fin.
6. The heat exchanger of claim 5 , wherein the header plates are made of a braze clad material.
7. The heat exchanger of claim 1 , wherein the fin has an offset geometry.
8. The heat exchanger of claim 1 , wherein the fin is made of a braze clad material.
9. The heat exchanger of claim 1 , wherein each integral fin passage provides a plurality of straight fluid flow passageways.
10. The heat exchanger of claim 1 , wherein the integral fin passages and the fin have a counter-flow or co-current flow arrangement.
11. A core of a plate-fin heat exchanger, the core comprising:
a plurality of integral fin passages, each integral fin passage having first and second plates and a plurality of extended surfaces extending between the first and second plates, the plates and the extended surfaces being integral, the plates and extended surfaces defining first passageways; and
a plurality of fins, each fin being located between and bonded to plates of adjacent integral fin passages, the plates and the fins defining second passageways.
12. The core of claim 11 , wherein at least one integral fin passage further includes a closure bar for an adjacent fin.
13. The core of claim 11 , further comprising closure bars for the fins, each closure bar being located between and bonded to plates of adjacent integral fin passages.
14. The core of claim 11 , further comprising first and second header plates, first ends of the integral fin passages fitting into slots in the first header plate, second ends of the integral fin passages fitting into slots in the second header plate, the header plates providing closure for the fins.
15. The core of claim 14 , wherein the header plates are made of a braze clad material.
16. The core of claim 11 , wherein the integral fin passages provide straight fluid flow passageways.
17. The core of claim 11 , wherein the fins are made of a braze clad material.
18. A method of constructing a heat exchanger, the method comprising:
providing a plurality of integral fin passages, each integral fin passage having been extruded to form plates and extended surfaces; and
locating fins between outer surfaces of adjacent integral fin passages; and
bonding the fins to the outer surfaces of the integral fin passages.
19. The method of claim 18 , further comprising the steps of mounting header plates to opposite ends of the integral fin passages; and bonding the header plates to the integral fin passages.
20. The method of claim 19 , further comprising the step of securing manifolds to the header plates and integral passages.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/557,347 US20020153129A1 (en) | 2000-04-25 | 2000-04-25 | Integral fin passage heat exchanger |
PCT/US2001/012965 WO2001081849A1 (en) | 2000-04-25 | 2001-04-23 | Integral fin passage heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/557,347 US20020153129A1 (en) | 2000-04-25 | 2000-04-25 | Integral fin passage heat exchanger |
Publications (1)
Publication Number | Publication Date |
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US20020153129A1 true US20020153129A1 (en) | 2002-10-24 |
Family
ID=24225032
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US09/557,347 Abandoned US20020153129A1 (en) | 2000-04-25 | 2000-04-25 | Integral fin passage heat exchanger |
Country Status (2)
Country | Link |
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US (1) | US20020153129A1 (en) |
WO (1) | WO2001081849A1 (en) |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2004068052A1 (en) | 2003-01-31 | 2004-08-12 | Heinz Schilling Kg | Air/water heat exchanger with partial water ways |
US20040173344A1 (en) * | 2001-05-18 | 2004-09-09 | David Averous | Louvered fins for heat exchanger |
US20070181294A1 (en) * | 2006-02-07 | 2007-08-09 | Jorg Soldner | Exhaust gas heat exchanger and method of operating the same |
US20090294110A1 (en) * | 2008-05-30 | 2009-12-03 | Foust Harry D | Spaced plate heat exchanger |
US8915292B2 (en) | 2006-02-07 | 2014-12-23 | Modine Manufacturing Company | Exhaust gas heat exchanger and method of operating the same |
US20170152816A1 (en) * | 2015-11-27 | 2017-06-01 | Hanon Systems | Fin - shaped - plate (fsp) egr cooler |
WO2017210602A1 (en) * | 2016-06-03 | 2017-12-07 | Flexenergy | Counter-flow heat exchanger |
US20200182552A1 (en) * | 2017-05-30 | 2020-06-11 | Shell Oil Company | Method of using an indirect heat exchanger and facility for processing liquefied natural gas comprising such heat exchanger |
EP4286780A1 (en) * | 2022-06-03 | 2023-12-06 | RTX Corporation | Conformal heat exchanger |
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BE1018518A3 (en) * | 2009-04-06 | 2011-02-01 | Atlas Copco Airpower Nv | IMPROVED HEAT EXCHANGER. |
AU2010273345B2 (en) | 2009-07-16 | 2013-02-21 | Lockheed Martin Corporation | Helical tube bundle arrangements for heat exchangers |
EP2454548B1 (en) * | 2009-07-17 | 2020-04-01 | Lockheed Martin Corporation | Heat exchanger and method for making |
US9777971B2 (en) | 2009-10-06 | 2017-10-03 | Lockheed Martin Corporation | Modular heat exchanger |
US9388798B2 (en) | 2010-10-01 | 2016-07-12 | Lockheed Martin Corporation | Modular heat-exchange apparatus |
US9670911B2 (en) | 2010-10-01 | 2017-06-06 | Lockheed Martin Corporation | Manifolding arrangement for a modular heat-exchange apparatus |
US9279626B2 (en) * | 2012-01-23 | 2016-03-08 | Honeywell International Inc. | Plate-fin heat exchanger with a porous blocker bar |
US9777970B2 (en) | 2013-08-09 | 2017-10-03 | Hamilton Sundstrand Coporation | Reduced thermal expansion closure bars for a heat exchanger |
US20190310031A1 (en) * | 2018-04-05 | 2019-10-10 | United Technologies Corporation | Secondarily applied cold side features for cast heat exchanger |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4276927A (en) * | 1979-06-04 | 1981-07-07 | The Trane Company | Plate type heat exchanger |
DE3668370D1 (en) * | 1985-10-25 | 1990-02-22 | Elpag Ag Chur | HEAT EXCHANGER. |
JP2884201B2 (en) * | 1991-08-02 | 1999-04-19 | 昭和アルミニウム株式会社 | Heat exchanger |
DE19519511A1 (en) * | 1994-05-31 | 1995-12-07 | Tjiok Mouw Ching | Heat exchanger using hollow plate |
-
2000
- 2000-04-25 US US09/557,347 patent/US20020153129A1/en not_active Abandoned
-
2001
- 2001-04-23 WO PCT/US2001/012965 patent/WO2001081849A1/en active Application Filing
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
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US20040173344A1 (en) * | 2001-05-18 | 2004-09-09 | David Averous | Louvered fins for heat exchanger |
WO2004068052A1 (en) | 2003-01-31 | 2004-08-12 | Heinz Schilling Kg | Air/water heat exchanger with partial water ways |
US20060153551A1 (en) * | 2003-01-31 | 2006-07-13 | Heinz Schilling | Air/water heat exchanger with partial water ways |
US20070181294A1 (en) * | 2006-02-07 | 2007-08-09 | Jorg Soldner | Exhaust gas heat exchanger and method of operating the same |
US8915292B2 (en) | 2006-02-07 | 2014-12-23 | Modine Manufacturing Company | Exhaust gas heat exchanger and method of operating the same |
US8020610B2 (en) * | 2006-02-07 | 2011-09-20 | Modine Manufacturing Company | Exhaust gas heat exchanger and method of operating the same |
US8079508B2 (en) | 2008-05-30 | 2011-12-20 | Foust Harry D | Spaced plate heat exchanger |
US20090294110A1 (en) * | 2008-05-30 | 2009-12-03 | Foust Harry D | Spaced plate heat exchanger |
US20170152816A1 (en) * | 2015-11-27 | 2017-06-01 | Hanon Systems | Fin - shaped - plate (fsp) egr cooler |
WO2017210602A1 (en) * | 2016-06-03 | 2017-12-07 | Flexenergy | Counter-flow heat exchanger |
US10222129B2 (en) | 2016-06-03 | 2019-03-05 | Flexenergy | Counter-flow heat exchanger |
US20200182552A1 (en) * | 2017-05-30 | 2020-06-11 | Shell Oil Company | Method of using an indirect heat exchanger and facility for processing liquefied natural gas comprising such heat exchanger |
EP4286780A1 (en) * | 2022-06-03 | 2023-12-06 | RTX Corporation | Conformal heat exchanger |
Also Published As
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WO2001081849A1 (en) | 2001-11-01 |
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Legal Events
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AS | Assignment |
Owner name: HONEYWELL INTERNATIONAL, INC., NEW JERSEY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:WHITE, STEPHEN L.;NAUMANN, BRIAN S.;REEL/FRAME:011126/0673 Effective date: 20000818 |
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