US20050155748A1 - Concentric tube heat exchanger end seal therefor - Google Patents
Concentric tube heat exchanger end seal therefor Download PDFInfo
- Publication number
- US20050155748A1 US20050155748A1 US11/080,902 US8090205A US2005155748A1 US 20050155748 A1 US20050155748 A1 US 20050155748A1 US 8090205 A US8090205 A US 8090205A US 2005155748 A1 US2005155748 A1 US 2005155748A1
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- United States
- Prior art keywords
- sealing member
- walls
- sealing
- wall
- tubes
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Classifications
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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
- F28F9/0234—Header boxes; End plates having a second heat exchanger disposed there within, e.g. oil cooler
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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
- 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
- F28D7/10—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 being arranged one within the other, e.g. concentrically
- F28D7/106—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 being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
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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
- F28F9/0202—Header boxes having their inner space divided by partitions
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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
- F28F2230/00—Sealing means
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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
A concentric tube heat exchanger comprises an outer tube and a concentric inner tube, with an annular passageway between the tubes. The ends of the annular passageway are sealed by sealing members having axially extending inner and outer walls which are connected to one another and which are sealed to the respective outer and inner tubes. The sealing member walls are preferably connected by an integrally formed connecting wall. The walls of the sealing member are preferably resilient and diverge so as to form a friction fit with the tubes during assembly of the heat exchanger. The heat exchanger further comprises a turbulizer which comprises a plurality of rows of corrugations defining axially extending flow passages. Preferably, the corrugations have a top land width greater than a bottom land width so that the side walls of the corrugation are radially arranged in the annular passageway. Adjacent corrugations in each row are preferably offset relative to one another by an amount of from about 30 percent to about 40 percent.
Description
- This invention relates to concentric tube heat exchangers, and more particularly to seals for closing an annular passageway between the inner and outer tubes of such heat exchangers.
- Concentric tube heat exchangers are commonly employed as transmission and transaxle oil coolers and are mounted in the coolant tank or manifold of a vehicle radiator. These heat exchangers include a cylindrical outer tube, a cylindrical inner tube and a turbulizer placed in an annular passageway between the inner and outer tubes. Oil is admitted to the annular passageway via an inlet port located at one end of the tube for passage through the turbulizer. The oil is cooled and exits via an outlet port located near the other end of the outer tube.
- Numerous arrangements are known in the prior art for sealing the ends of the annular passageway. These include deformation of the inner and/or outer tubes, for example as shown in U.S. Pat. No. 3,001,767 (Straubing), U.S. Pat. No. 5,732,769 (Staffa) and U.S. Pat. No. 5,950,716 (Appelquist et al.); or by use of annular seals as described in U.S. Pat. Nos. 3,323,586 and 3,339,260 (Burne et al.)
- The suitability of prior art end sealing methods can be affected by the type of material from which the heat exchanger is made. For example, in aluminum concentric tube heat exchangers, it has proven difficult to seal the annular passageway by deformation of the tubes. This has led some manufacturers to seal the annular passageway with machined aluminum end blocks, which significantly increase the weight and cost of the heat exchanger.
- Accordingly, there is a need for improved methods for sealing the annular passageway in a concentric tube heat exchanger which will provide economical and reliable sealing in a variety of materials.
- In one aspect, the present invention provides a concentric tube heat exchanger having a first end and a second end. The heat exchanger comprises an outer tube and an inner tube. The inner tube is received inside the outer tube and concentric therewith, wherein an annular passageway is formed between the inner and outer tubes. The heat exchanger further comprises first and second annular sealing members received inside the annular passageway between the inner and outer tubes. The first sealing member is positioned proximate the first end of the heat exchanger and the second sealing member is positioned proximate the second end of the heat exchanger. Each of the sealing members comprises an outer wall and an inner wall which are connected to one another, each of the walls having first and second axially-spaced ends, the outer wall being sealed to the outer tube and the inner wall being sealed to the inner tube, thereby sealing the ends of the tubes.
- The concentric tube heat exchanger according to the invention further comprises a turbulizer received in the annular passageway between the tubes. The turbulizer comprises a plurality of corrugations defining a plurality of axially extending flow passages extending parallel to the tubes. Each of the corrugations comprises a top land, a bottom land and a pair of side surfaces connecting the top and bottom lands, the top land being in heat exchange contact with the outer tube and the bottom land being in heat exchange contact with the inner tube. The convolutions are arranged in axially extending rows with the convolutions in each row being connected to one another and with an offset being provided between adjacent convolutions in each row. The offset has a width which is from about 30 percent to about 40 percent of a width of the top land or the bottom land.
- In another aspect, the present invention provides a sealing member for sealing opposite ends of an annular passageway extending along an axis between inner and outer tubes of a concentric tube heat exchanger. The sealing member comprises an outer wall and an inner wall. The outer wall has first and second axially-spaced ends and a generally axially-extending portion between its ends for sealing to the outer tube. The inner wall has first and second axially-spaced ends, is connected to the outer wall and is spaced radially inwardly of the outer wall. The inner wall has a generally axially-extending portion between its ends for sealing to the inner tube. The generally axially-extending portions of the walls diverge from one another along said axis.
- The invention will now be described, by way of example only, with reference to the accompanying drawings, in which:
-
FIG. 1 is a perspective view of a preferred heat exchanger according to the invention, prior to insertion of the sealing members; -
FIG. 2 is a cross section through one of the sealing members along line II-II inFIG. 1 ; -
FIGS. 3A to 3D are cross sections through alternate preferred sealing members according to the invention; -
FIG. 4 is a cross section in an axial plane through one end of the heat exchanger ofFIG. 1 , after insertion of the sealing members; -
FIG. 5 is a close-up of area A inFIG. 4 ; -
FIG. 6 is a cross-section along line VI-VI ofFIG. 1 ; -
FIG. 7 is a front view of a portion of a turbulizer sheet according to the invention; and -
FIG. 8 is a top plan view of a portion of the turbulizer sheet ofFIG. 7 . -
FIG. 1 illustrates a preferred concentrictube heat exchanger 10 according to the invention.Heat exchanger 10 comprises an outercylindrical tube 12 and an innercylindrical tube 14, theinner tube 14 being received in theouter tube 12 and concentric therewith, with anannular passageway 16 being formed between the outer andinner tubes heat exchanger 10. -
Heat exchanger 10 further comprises aninlet port 18 located adjacent itsfirst end 20 and an outlet port 22 (FIG. 6 ) located adjacent itssecond end 24. Both the inlet andoutlet ports outer tube 12 through which a fluid to be cooled, such as oil, is allowed to enter and exit theannular passageway 16. Theheat exchanger 10 further comprises aninlet filting 26 and anoutlet filting 28 which are mounted to the outer surface of theouter tube 12 in communication with the inlet andoutlet ports filtings outer tube 12, the areas surrounding inlet andoutlet ports FIG. 6 . Sealed connections are formed betweenfiltings tube 12, for example by brazing. - Not shown in
FIG. 1 , but described in detail below, is aturbulizer 30 which is received in theannular passageway 16 and extends through theannular passageway 16 between the inlet andoutlet ports - Lastly, the
heat exchanger 10 comprises a pair ofannular sealing members 32 for sealing the ends of theannular passageway 16. InFIG. 1 , theheat exchanger 10 is shown in a partially disassembled state with the sealingmembers 32 separated from thetubes FIG. 4 illustrates the first end ofheat exchanger 10 in its assembled state with a sealingmember 32 received in theannular passageway 16 and brazed to both the outer andinner tubes - As shown in
FIG. 4 , sealingmember 32 is received inside theannular passageway 16 between the outer andinner tubes member 32 is located proximate thefirst end 20 ofheat exchanger 10 and, more particularly, is located between theinlet port 18 and thefirst end 20 of theheat exchanger 10. The sealingmember 32 is sealingly connected to both the inner surface of theouter tube 12 and the outer surface of theinner tube 14, preferably by brazing, withbraze fillets sealing member 32 and theouter tube 12, andbraze fillets member 32 and theinner tube 14. Thebraze fillets FIG. 5 . It will be appreciated that thesecond end 24 ofheat exchanger 10 is preferably sealed in an identical manner with the other sealingmember 32 illustrated inFIG. 1 . - The
preferred sealing members 32 shown in the drawings each comprise anouter wall 42 and aninner wall 48, with theinner wall 48 being spaced radially inwardly of theouter wall 42, and preferably concentric therewith. Theouter wall 42 has afirst end 46 and asecond end 44, the ends 44, 46 being axially spaced from one another, with at least a portion of the outer wall extending generally along the axis. Similarly, the inner wall has afirst end 52 and asecond end 50, the ends 50, 52 being axially spaced from one another, with at least a portion of the outer wall extending generally along the axis. In the sealingmembers 32 shown in the drawings, the entire outer andinner walls inner wall 48 abutting the outer surface ofinner tube 14 and sealed thereto, and with theouter wall 42 abutting the inner surface ofouter tube 12 and sealed thereto. However, it will be appreciated that this is not necessary that the entire outer andinner walls walls inner tubes - The sealing
members 32 illustrated in the drawings are of generally U-shaped cross section, with thefirst end 46 of theouter wall 42 being connected to thefirst end 52 of theinner wall 48 by a radially extending connectingportion 54 which seals the radial space between thewalls walls portion 54 is integrally formed with thewalls - As shown in
FIG. 2 , the outer andinner walls walls walls portion 54 toward the second ends 44, 50 such that a radial distance measured between thewalls portion 54 is less than a radial distance measured between the second ends 44, 50 ofwalls walls members 32 are inserted into the annular passageway with the connectingportions 54 spaced inwardly of theends walls 42, 48 (as shown inFIG. 4 ), the second ends 44, 50 become compressed so that the sealingmember walls respective tubes members 32 during the assembly process. The angle at which thewalls members 32 into theannular passageway 16 with a friction fit, while ensuring substantially complete contact between thewalls tubes side walls - As shown in
FIG. 4 , the sealingmember 32 is preferably spaced inwardly from theend 20 of theheat exchanger 10, for at least two reasons. Firstly, it will be noted fromFIG. 4 that theturbulizer 30 does not extend past theinlet port 18 and, in fact, is prevented from doing so by acollar 56 of inlet fitting 26, thecollar 56 projecting into theannular passageway 16 through theinlet port 18 and acting as a stop for theturbulizer 30. Thus, theturbulizer 30 does not provide support for the portion ofannular passageway 16 extending from theinlet port 18 to thefirst end 20 of theheat exchanger 10. To minimize the unsupported area ofannular passageway 16 and thereby avoid narrowing of theannular passageway 16 in the area surroundinginlet port 18, the sealingmember 32 is located inwardly of theend 20 ofheat exchanger 10, between theinlet port 18 and theend 20. Secondly, locating the sealing member inward of theend 20 ensures that there is sufficient area for formation ofbraze fillets 34 between the top 44 ofouter wall 42 and the inner surface ofouter tube 12, and between the top 50 ofinner tube 14 and the outer surface ofinner tube 14. The formation of continuous braze fillets about the entire circumference of each sealing member ensures robust, leak proof joints at theends - As shown in
FIG. 2 , the connectingportion 54 of the sealing member is preferably flat and extends radially between the outer andinner walls member 32.FIG. 3A illustrates an alternate preferred form of sealingmember 58 having outer andinner walls portion 64. It will also be appreciated that numerous alternate constructions of sealing members are possible without departing from the present invention. For example, as shown inFIG. 3B , a sealingmember 132 may be of generally H-shaped cross section, with the connectingmember 154 extending radially between the sealingmember walls FIG. 3C shows a sealing member 232 which is of generally V-shaped cross section, and in which a V-shaped connectingmember 254 extends between sealingmember walls FIG. 3D shows a sealingmember 332 which is of modified U-shaped construction, having a somewhat indented connectingportion 354 extending between the outer andinner walls - In a particularly preferred embodiment of the present invention, all the components of
heat exchanger 10 are formed from aluminum or alloys thereof, and are preferably formed from brazeable aluminum alloys. In particular, thetubes outer tube 12 and the outer surface of theinner tube 14, i.e. the “oil-side” surfaces, are clad with a brazing alloy, while the opposite surfaces of these tubes, i.e. the “water-side” surfaces, are clad with an alloy containing an amount of zinc for sacrificial corrosion protection. Where the oil-side surfaces oftubes turbulizer 30 nor the sealingmembers 32 require a cladding of brazing alloy. It will be appreciated that alternate arrangements are possible, for example, theturbulizer 30 and sealingmembers 32 may be clad with brazing alloy, and thetubes heat exchanger 10 may be comprised of non-clad aluminum members, and the filler metal for brazing may be provided by means of a brazing paste or preform, and brazing can be accomplished by either flux or fluxless brazing by suitable selection of the braze system and materials. Similarly, a brazing paste or preform can be used to join thefittings outer tube 12. - It will be appreciated that the sealing
members 32 may be installed with the second ends 44, 50 ofwalls outlet port members 32 are received in the annular passageway with the second ends 44, 50 ofwalls heat exchanger 10, as shown in the drawings. - The
heat exchanger 10 is preferably by assembled by inserting theinner tube 14 and theturbulizer 30 into theouter tube 12, inserting the sealingmembers 32 into the opposite ends 20 and 22, expanding the inner tube so that both the outer andinner tubes turbulizer 30, applying the fittings to the outer tube, and then brazing the assembly in a brazing oven. - A preferred form of
turbulizer 30 is now described below with reference toFIGS. 7 and 8 .Turbulizer 30 is of generally the same construction as the turbulizer described in U.S. Pat. No. Re. 35,890 (So), which is incorporated herein by reference in its entirety. In particular, prior to insertion into theannular passageway 16, theturbulizer 30 is in the form of a sheet having a plurality ofconvolutions 74 which define a plurality of flow passages. The flow passages extend axially (parallel to arrow A inFIG. 8 ) once theturbulizer 30 is rolled up and inserted into theannular passageway 16. Each of theconvolutions 74 has a height H (FIG. 7 ), a length L (FIG. 8 ), a rectangulartop land 76 having width WT (FIGS. 7 and 8 ), a rectangularbottom land 78 having a width WB, and a pair of side surfaces 80 extending between the top and bottom lands 76, 78. In a particularly preferred embodiment of the present invention, theconvolutions 74 have a height of about 3 mm and a length of at least about 1.6 mm. It will be appreciated that all width dimensions described herein are measured perpendicular to the axial direction. - The top lands 76 of the
convolutions 74 are arranged in axially extending rows, as seen inFIG. 8 , which shows asingle row 82 ofconvolutions 74. The top lands 76 of theconvolutions 74 in eachrow 82 are connected to one another along their front and rear edges at areas 84 (FIG. 8 ) and are offset relative to one another, with the width of the offset being WO (FIG. 8 ). It will be appreciated that a bottom plan view of theturbulizer 30 has an appearance which is substantially the same as that shown inFIG. 8 . - The features of
turbulizer 30 described above are also present in the turbulizer described in the above-mentioned So patent. Theturbulizer 30 according to the invention differs from the So turbulizer in several important respects, which are now discussed below. - Firstly, the
turbulizer 30 according to the invention has a preferred offset WO which is significantly less than that of the So turbulizer, thereby maximizing the width of thearea 84 along which theconvolutions 84 are connected with one another. In the So turbulizer, the width of offset is about 50 percent of the width of the top and bottom lands, whereas the offset in theturbulizer 30 according to the invention is about 30 to 40 percent (i.e. WO/WT or WB=0.30-0.40), preferably about 31 to about 36 percent. The inventors have found that decreasing the offset of theconvolutions 74 helps to ensure formability of the turbulizer 30 from metals such as aluminum, while providing high heat transfer and low pressure drop. - Secondly, the
turbulizer 30 according to the invention is formed with the top land width WT which is greater than the bottom land with WB, and with the side surfaces 80 of eachconvolution 74 sloping away from one another from thetop land 76 to thebottom land 78. Thus, when theturbulizer sheet 30 is rolled up and inserted into theannular passageway 16 with the bottom lands 78 in heat exchange contact with theinner tube 14 and the top lands 76 in heat exchange contact with theouter tube 12, the side surfaces 80 are extend substantially radially between theouter tube 12 andinner tube 14, producing axial flow passages of substantially constant cross-sectional area. This helps to maximize heat transfer and minimize pressure drop. - In a particularly preferred embodiment of the invention, the side surfaces are sloped at about 5° from vertical, the top land width WT is about 1.1 mm, the bottom land width WB is about 1.0 mm, the centers of
rows 82 are spaced about 2.1 mm apart, and the offset with WO is about 0.35 mm. In a turbulizer having these dimensions, the offset expressed as a percentage of the top land width is about 31 percent and the offset expressed as a percentage of the bottom land width is about 36 percent. - The above-mentioned features of the turbulizer according to the invention, for example the top and bottom lands of different width, the radially extending side surfaces, and the decreased offset, ensure optimum fit-up of the turbulizer during assembly, thereby maximizing metal-to-metal contact between the turbulizer and the tubes, which ensures brazeability and optimum heat transfer.
- Although the invention has been described in connection with certain preferred embodiments, it is not intended to be limited thereto. Rather, the invention includes all embodiments which may fall within the scope of the following claims.
Claims (21)
1-17. (canceled)
18. A sealing member for sealing an annular gap between inner and outer axially-extending tubes of a concentric tube heat exchanger, the sealing member comprising:
an outer wall having first and second axially-spaced ends and having a generally axially-extending portion between its ends for sealing to the outer tube; and
an inner wall having first and second axially-spaced ends, the inner wall being connected to the outer wall and being spaced radially inwardly of the outer wall, the inner wall having a generally axially-extending portion between its ends for sealing to the inner tube;
wherein the generally axially-extending portions of the walls diverge from one another along said axis.
19. The sealing member of claim 18 , wherein the inner and outer walls are connected through a connecting portion, the second ends of the sealing member walls are axially spaced from the connecting portion which seals a radial space between the sealing member walls.
20. The sealing member of claim 18 , wherein the generally axially-extending portions of the walls are resilient, and wherein the generally axially-extending portions diverge from one another at an angle such that, when the sealing member is received in the annular gap with the outer wall frictionally engaging the outer tube and the inner wall frictionally engaging the inner tube, and such that the generally axially-extending portions of the sealing member walls are in substantial engagement with the inner and outer tubes.
21. The sealing member of claim 18 , wherein the generally axially-extending portion of at least one of the sealing member walls diverges from the axis by an angle of from about 1 to about 2 degrees.
22. The sealing member of claim 18 , wherein the generally axially-extending portions of the inner and outer sealing member walls diverge from the axis by an angle of from about 1 to about 2 degrees.
23. The sealing member of claim 21 , wherein said angle is about 1.5 degrees.
24. The sealing member of claim 22 , wherein said angle is about 1.5 degrees.
25. The sealing member of claim 19 , wherein the sealing member is generally U-shaped, with the first ends of the sealing member walls being connected to the connecting portion and the second ends of the sealing member walls being distal to the connecting portion.
26. The sealing member of claim 25 , wherein the connecting portion is rounded.
27. The sealing member of claim 25 , wherein the connecting portion is flat and extends radially between the inner and outer walls.
28. The sealing member of claim 25 , wherein the connecting portion is V-shaped.
29. The sealing member of claim 25 , wherein the connecting portion is indented toward the second end of the outer wall.
30. The sealing member of claim 19 , wherein the connecting portion is attached to the sealing member walls between the first and second ends, such that the sealing member is generally H-shaped.
31. The sealing member of claim 19 , wherein the connecting portion is integrally formed with the sealing member walls.
32. The sealing member of claim 18 , wherein the walls are formed from a material which is sufficiently resilient such that the second ends of the first and second walls are compressible toward one another.
33. The sealing member of claim 32 , wherein the walls are comprised of aluminum.
34. A method of manufacturing a concentric tube heat exchanger comprising inner and outer axially-extending tubes and an axially-extending annular passageway between the tubes, the method comprising:
(a) providing a pair of annular sealing members, each of the sealing members comprising a resilient outer wall having a first end and a second end, a resilient inner wall having a first and a second end and being spaced from the outer wall, and a connecting portion through which the inner and outer walls are connected;
(b) inserting the sealing members into opposite ends of the annular passageway such that at least a portion of the inner wall and at least a portion of the outer wall of the sealing members are generally axially aligned, wherein the inner and outer walls are compressed toward one another during insertion of the sealing members into the annular passageway, such that the generally axially-aligned portions of the inner and outer walls frictionally engage the inner and outer tubes, respectively; and
(c) expanding the inner tube such that the generally axially-extending portions of the inner and outer walls of the sealing member are parallel to one another and are in substantially complete contact with the inner and outer tubes, respectively.
35. The method of claim 34 , wherein the tubes and the sealing members are comprised of aluminum and wherein the method further comprises:
(d) brazing the generally axially-extending portions of the sealing member walls to the inner and outer tubes.
36. The method of claim 35 , wherein the tubes and/or the sealing members are provided with a cladding comprised of a brazing alloy, at least on surfaces at which the sealing members and the tubes are brazed together.
37. The method of claim 34 , wherein the annular passageway has open ends through which the sealing members are inserted, and wherein the sealing members are inserted inwardly of the ends of the annular passageway.
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US11/080,902 US20050155748A1 (en) | 2003-08-29 | 2005-03-14 | Concentric tube heat exchanger end seal therefor |
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US10/652,768 US20050045315A1 (en) | 2003-08-29 | 2003-08-29 | Concentric tube heat exchanger and end seal therefor |
US11/080,902 US20050155748A1 (en) | 2003-08-29 | 2005-03-14 | Concentric tube heat exchanger end seal therefor |
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US10/652,768 Division US20050045315A1 (en) | 2003-08-29 | 2003-08-29 | Concentric tube heat exchanger and end seal therefor |
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US11/080,902 Abandoned US20050155748A1 (en) | 2003-08-29 | 2005-03-14 | Concentric tube heat exchanger end seal therefor |
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US20120222849A1 (en) * | 2011-03-02 | 2012-09-06 | Yen-Ti Liu | Oil-Cooling Tube |
US20120318483A1 (en) * | 2011-06-14 | 2012-12-20 | David Cosby | Heat Exchanger for Drain Heat Recovery |
US8474515B2 (en) | 2009-01-16 | 2013-07-02 | Dana Canada Corporation | Finned cylindrical heat exchanger |
GB2498820A (en) * | 2012-04-05 | 2013-07-31 | R B Radley & Co Ltd | Condenser |
US20140245768A1 (en) * | 2013-03-04 | 2014-09-04 | Rocky Research | Co-fired absorption system generator |
US8944155B2 (en) | 2010-07-15 | 2015-02-03 | Dana Canada Corporation | Annular axial flow ribbed heat exchanger |
IT201800004827A1 (en) * | 2018-04-24 | 2019-10-24 | DOUBLE PIPE HEAT EXCHANGER AND ITS MANUFACTURING METHOD | |
CN113187898A (en) * | 2020-01-14 | 2021-07-30 | 国家电投集团科学技术研究院有限公司 | Sealing device for small penetrating piece on cavity and heat exchanger with sealing device |
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Cited By (15)
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US8474515B2 (en) | 2009-01-16 | 2013-07-02 | Dana Canada Corporation | Finned cylindrical heat exchanger |
US8944155B2 (en) | 2010-07-15 | 2015-02-03 | Dana Canada Corporation | Annular axial flow ribbed heat exchanger |
US20120222849A1 (en) * | 2011-03-02 | 2012-09-06 | Yen-Ti Liu | Oil-Cooling Tube |
US20120318483A1 (en) * | 2011-06-14 | 2012-12-20 | David Cosby | Heat Exchanger for Drain Heat Recovery |
US10704837B2 (en) | 2012-04-05 | 2020-07-07 | R.B. Radley & Company Limited | Laboratory condensers with passive heat exchange |
GB2498820A (en) * | 2012-04-05 | 2013-07-31 | R B Radley & Co Ltd | Condenser |
WO2013150318A1 (en) | 2012-04-05 | 2013-10-10 | R.B. Radley & Company Limited | Laboratory condensers with passive heat exchange |
GB2498820B (en) * | 2012-04-05 | 2014-04-16 | R B Radley & Co Ltd | Condensers |
US20140245768A1 (en) * | 2013-03-04 | 2014-09-04 | Rocky Research | Co-fired absorption system generator |
US9664451B2 (en) * | 2013-03-04 | 2017-05-30 | Rocky Research | Co-fired absorption system generator |
IT201800004827A1 (en) * | 2018-04-24 | 2019-10-24 | DOUBLE PIPE HEAT EXCHANGER AND ITS MANUFACTURING METHOD | |
WO2019207384A1 (en) | 2018-04-24 | 2019-10-31 | Manenti Giovanni | Double-tube heat exchanger and manufacturing method thereof |
RU2771115C1 (en) * | 2018-04-24 | 2022-04-26 | Джованни МАНЕНТИ | Dual-pipe heat exchanger and method for manufacture thereof |
US11668529B2 (en) | 2018-04-24 | 2023-06-06 | Giovanni MANENTI | Double-tube heat exchanger and manufacturing method thereof |
CN113187898A (en) * | 2020-01-14 | 2021-07-30 | 国家电投集团科学技术研究院有限公司 | Sealing device for small penetrating piece on cavity and heat exchanger with sealing device |
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