US20050045315A1 - Concentric tube heat exchanger and end seal therefor - Google Patents
Concentric tube heat exchanger and end seal therefor Download PDFInfo
- Publication number
- US20050045315A1 US20050045315A1 US10/652,768 US65276803A US2005045315A1 US 20050045315 A1 US20050045315 A1 US 20050045315A1 US 65276803 A US65276803 A US 65276803A US 2005045315 A1 US2005045315 A1 US 2005045315A1
- Authority
- US
- United States
- Prior art keywords
- heat exchanger
- sealing member
- walls
- tubes
- sealing
- 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
Links
Images
Classifications
-
- 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
-
- 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
-
- 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
-
- 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
Definitions
- 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.
- 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 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.
- 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.
- 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 in FIG. 1 ;
- FIGS. 3A to 3 D 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 of FIG. 1 , after insertion of the sealing members;
- FIG. 5 is a close-up of area A in FIG. 4 ;
- FIG. 6 is a cross-section along line VI-VI of FIG. 1 ;
- FIG. 7 is a front view of a portion of a turbulizer sheet according to the invention.
- FIG. 8 is a top plan view of a portion of the turbulizer sheet of FIG. 7 .
- FIG. 1 illustrates a preferred concentric tube heat exchanger 10 according to the invention.
- Heat exchanger 10 comprises an outer cylindrical tube 12 and an inner cylindrical tube 14 , the inner tube 14 being received in the outer tube 12 and concentric therewith, with an annular passageway 16 being formed between the outer and inner tubes 12 , 14 and extending through substantially the entire length of the heat exchanger 10 .
- Heat exchanger 10 further comprises an inlet port 18 located adjacent its first end 20 and an outlet port 22 ( FIG. 6 ) located adjacent its second end 24 . Both the inlet and outlet ports 18 , 22 comprise perforations formed in the outer tube 12 through which a fluid to be cooled, such as oil, is allowed to enter and exit the annular passageway 16 .
- the heat exchanger 10 further comprises an inlet fitting 26 and an outlet fitting 28 which are mounted to the outer surface of the outer tube 12 in communication with the inlet and outlet ports 18 , 22 respectively.
- the areas surrounding inlet and outlet ports 18 , 22 are preferably flattened, as shown in FIG. 6 . Sealed connections are formed between fittings 26 , 28 and the outer surface of tube 12 , for example by brazing.
- a turbulizer 30 which is received in the annular passageway 16 and extends through the annular passageway 16 between the inlet and outlet ports 18 , 22 .
- the heat exchanger 10 comprises a pair of annular sealing members 32 for sealing the ends of the annular passageway 16 .
- FIG. 1 the heat exchanger 10 is shown in a partially disassembled state with the sealing members 32 separated from the tubes 12 , 14 .
- FIG. 4 illustrates the first end of heat exchanger 10 in its assembled state with a sealing member 32 received in the annular passageway 16 and brazed to both the outer and inner tubes 12 , 14 .
- sealing member 32 is received inside the annular passageway 16 between the outer and inner tubes 12 , 14 .
- the sealing member 32 is located proximate the first end 20 of heat exchanger 10 and, more particularly, is located between the inlet port 18 and the first end 20 of the heat exchanger 10 .
- the sealing member 32 is sealingly connected to both the inner surface of the outer tube 12 and the outer surface of the inner tube 14 , preferably by brazing, with braze fillets 34 and 36 being formed between the sealing member 32 and the outer tube 12 , and braze fillets 38 and 40 being formed between the sealing member 32 and the inner tube 14 .
- the braze fillets 34 , 36 , 38 and 40 are shown only in the close-up of FIG. 5 . It will be appreciated that the second end 24 of heat exchanger 10 is preferably sealed in an identical manner with the other sealing member 32 illustrated in FIG. 1 .
- the preferred sealing members 32 shown in the drawings each comprise an outer wall 42 and an inner wall 48 , with the inner wall 48 being spaced radially inwardly of the outer wall 42 , and preferably concentric therewith.
- the outer wall 42 has a first end 46 and a second 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.
- the inner wall has a first end 52 and a second 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.
- the entire outer and inner walls 42 and 46 extend along the axis, with the inner wall 48 abutting the outer surface of inner tube 14 and sealed thereto, and with the outer wall 42 abutting the inner surface of outer tube 12 and sealed thereto.
- this is not necessary that the entire outer and inner walls 42 , 48 extend generally axially. Rather, it will be appreciated that only portions of walls 42 , 46 are required to extend axially, sufficient to form seals with the outer and inner tubes 12 , 14 , respectively.
- the sealing members 32 illustrated in the drawings are of generally U-shaped cross section, with the first end 46 of the outer wall 42 being connected to the first end 52 of the inner wall 48 by a radially extending connecting portion 54 which seals the radial space between the walls 42 , 48 .
- the second ends 44 , 50 of the walls 42 , 48 are distal to the connecting portion.
- the connecting portion 54 is integrally formed with the walls 42 , 48 .
- the outer and inner walls 42 , 48 of the sealing member are not necessarily parallel to one another. Rather it is preferred that the walls 42 , 48 , or the generally axially extending portions thereof, diverge from one another along the axis. Preferably, the walls 42 , 48 diverge from one another from the connecting portion 54 toward the second ends 44 , 50 such that a radial distance measured between the walls 42 , 48 at the connecting portion 54 is less than a radial distance measured between the second ends 44 , 50 of walls 42 , 48 .
- the material from which the walls 42 , 48 are formed is preferably sufficiently resilient such that, when the sealing members 32 are inserted into the annular passageway with the connecting portions 54 spaced inwardly of the ends 20 , 24 by a greater distance than the second ends 44 , 50 of walls 42 , 48 (as shown in FIG. 4 ), the second ends 44 , 50 become compressed so that the sealing member walls 42 , 48 frictionally engage the respective tubes 12 , 14 , thereby retaining the sealing members 32 during the assembly process.
- the angle at which the walls 42 , 48 diverge is sufficient for easy insertion of the sealing members 32 into the annular passageway 16 with a friction fit, while ensuring substantially complete contact between the walls 42 , 48 and the tubes 12 , 14 after the inner tube is expanded during the manufacturing process, thus ensuring leak-proof braze joints.
- the inventors have found that these objects can be achieved by forming sealing members with at least one, and preferably both, side walls 42 , 48 diverging from the axis by an angle ⁇ of from about 1 to about 2 degrees, more preferably about 1.5 degrees.
- the sealing member 32 is preferably spaced inwardly from the end 20 of the heat exchanger 10 , for at least two reasons. Firstly, it will be noted from FIG. 4 that the turbulizer 30 does not extend past the inlet port 18 and, in fact, is prevented from doing so by a collar 56 of inlet fitting 26 , the collar 56 projecting into the annular passageway 16 through the inlet port 18 and acting as a stop for the turbulizer 30 . Thus, the turbulizer 30 does not provide support for the portion of annular passageway 16 extending from the inlet port 18 to the first end 20 of the heat exchanger 10 .
- the sealing member 32 is located inwardly of the end 20 of heat exchanger 10 , between the inlet port 18 and the end 20 .
- locating the sealing member inward of the end 20 ensures that there is sufficient area for formation of braze fillets 34 between the top 44 of outer wall 42 and the inner surface of outer tube 12 , and between the top 50 of inner tube 14 and the outer surface of inner tube 14 .
- the formation of continuous braze fillets about the entire circumference of each sealing member ensures robust, leak proof joints at the ends 20 , 24 of the heat exchanger.
- FIG. 3A illustrates an alternate preferred form of sealing member 58 having outer and inner walls 60 , 62 diverging from the axis by an angle ⁇ and connected at their bottoms by a rounded connecting portion 64 .
- a sealing member 132 may be of generally H-shaped cross section, with the connecting member 154 extending radially between the sealing member walls 142 , 148 intermediate the first ends 146 , 152 and the second ends 144 , 150 .
- FIG. 3C shows a sealing member 232 which is of generally V-shaped cross section, and in which a V-shaped connecting member 254 extends between sealing member walls 242 , 248 , which extend generally axially.
- FIG. 3D shows a sealing member 332 which is of modified U-shaped construction, having a somewhat indented connecting portion 354 extending between the outer and inner walls 342 , 348 .
- all the components of heat exchanger 10 are formed from aluminum or alloys thereof, and are preferably formed from brazeable aluminum alloys.
- the tubes 12 , 14 are preferably of welded and drawn construction and comprise an aluminum alloy core layer clad on at least one side with an aluminum brazing alloy. More preferably, the inner surface of the outer tube 12 and the outer surface of the inner 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.
- the turbulizer 30 and sealing members 32 may be clad with brazing alloy, and the tubes 12 , 14 may be unclad. Alternatively, all these components may be clad with a brazing alloy.
- the 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.
- a brazing paste or preform can be used to join the fittings 26 , 28 to the corrosion resistant clad water-side surface of the outer tube 12 .
- sealing members 32 may be installed with the second ends 44 , 50 of walls 42 , 48 facing the inlet or outlet port 18 , 22 . However, for manufacturing purposes, it is preferred that the sealing members 32 are received in the annular passageway with the second ends 44 , 50 of walls 42 , 48 facing the ends 20 , 24 of heat exchanger 10 , as shown in the drawings.
- the heat exchanger 10 is preferably by assembled by inserting the inner tube 14 and the turbulizer 30 into the outer tube 12 , inserting the sealing members 32 into the opposite ends 20 and 22 , expanding the inner tube so that both the outer and inner tubes 12 , 14 are in intimate heat exchange contact with the turbulizer 30 , applying the fittings to the outer tube, and then brazing the assembly in a brazing oven.
- 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.
- the turbulizer 30 prior to insertion into the annular passageway 16 , the turbulizer 30 is in the form of a sheet having a plurality of convolutions 74 which define a plurality of flow passages.
- the flow passages extend axially (parallel to arrow A in FIG. 8 ) once the turbulizer 30 is rolled up and inserted into the annular passageway 16 .
- Each of the convolutions 74 has a height H ( FIG.
- the convolutions 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 in FIG. 8 , which shows a single row 82 of convolutions 74 .
- the top lands 76 of the convolutions 74 in each row 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 W O ( FIG. 8 ).
- a bottom plan view of the turbulizer 30 has an appearance which is substantially the same as that shown in FIG. 8 .
- turbulizer 30 The features of turbulizer 30 described above are also present in the turbulizer described in the above-mentioned So patent.
- the turbulizer 30 according to the invention differs from the So turbulizer in several important respects, which are now discussed below.
- the turbulizer 30 according to the invention has a preferred offset W O which is significantly less than that of the So turbulizer, thereby maximizing the width of the area 84 along which the convolutions 84 are connected with one another.
- the width of offset is about 50 percent of the width of the top and bottom lands
- the inventors have found that decreasing the offset of the convolutions 74 helps to ensure formability of the turbulizer 30 from metals such as aluminum, while providing high heat transfer and low pressure drop.
- the turbulizer 30 is formed with the top land width W T which is greater than the bottom land with W B , and with the side surfaces 80 of each convolution 74 sloping away from one another from the top land 76 to the bottom land 78 .
- W T top land width
- W B bottom land with W B
- the side surfaces 80 are extend substantially radially between the outer tube 12 and inner tube 14 , producing axial flow passages of substantially constant cross-sectional area. This helps to maximize heat transfer and minimize pressure drop.
- the side surfaces are sloped at about 5° from vertical, the top land width W T is about 1.1 mm, the bottom land width W B is about 1.0 mm, the centers of rows 82 are spaced about 2.1 mm apart, and the offset with W O is about 0.35 mm.
- 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 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.
Landscapes
- 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)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA2439023A CA2439023C (fr) | 2003-08-29 | 2003-08-29 | Echangeur de chaleur a tubes concentriques et embout d'etancheite connexe |
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 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA2439023A CA2439023C (fr) | 2003-08-29 | 2003-08-29 | Echangeur de chaleur a tubes concentriques et embout d'etancheite connexe |
US10/652,768 US20050045315A1 (en) | 2003-08-29 | 2003-08-29 | Concentric tube heat exchanger and end seal therefor |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/080,902 Division US20050155748A1 (en) | 2003-08-29 | 2005-03-14 | Concentric tube heat exchanger end seal therefor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20050045315A1 true US20050045315A1 (en) | 2005-03-03 |
Family
ID=34436133
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/652,768 Abandoned US20050045315A1 (en) | 2003-08-29 | 2003-08-29 | Concentric tube heat exchanger and end seal therefor |
Country Status (2)
Country | Link |
---|---|
US (1) | US20050045315A1 (fr) |
CA (1) | CA2439023C (fr) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9459052B2 (en) | 2011-03-01 | 2016-10-04 | Dana Canada Corporation | Coaxial gas-liquid heat exchanger with thermal expansion connector |
CN112005071A (zh) * | 2018-04-24 | 2020-11-27 | G·玛南蒂 | 双管热交换器及其制造方法 |
US11029095B2 (en) * | 2015-07-30 | 2021-06-08 | Senior Uk Limited | Finned coaxial cooler |
Citations (46)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2468909A (en) * | 1946-01-03 | 1949-05-03 | Cnossen | Auxiliary air heater |
US2692763A (en) * | 1952-03-08 | 1954-10-26 | Air Preheater | Supporting spacer for annular corrugated fins |
US2693026A (en) * | 1950-02-17 | 1954-11-02 | Modine Mfg Co | Method of making concentric tubes with radial fins |
US2703921A (en) * | 1949-04-14 | 1955-03-15 | Brown Fintube Co | Method of making internally finned tubes |
US2712438A (en) * | 1951-04-27 | 1955-07-05 | Brown Fintube Co | Heat exchanger |
US2726681A (en) * | 1950-09-18 | 1955-12-13 | Brown Fintube Co | Internally finned tube |
US2731709A (en) * | 1950-09-18 | 1956-01-24 | Brown Fintube Co | Method of making internally finned heat exchanger tubes |
US2752128A (en) * | 1955-10-17 | 1956-06-26 | Modine Mfg Co | Heat exchange structure |
US2756032A (en) * | 1952-11-17 | 1956-07-24 | Heater | |
US3001767A (en) * | 1959-11-16 | 1961-09-26 | Kenmore Machine Products Inc | Tubular structure |
US3126918A (en) * | 1964-03-31 | Slip ring spacer for insulated conduit systems | ||
US3323586A (en) * | 1964-10-14 | 1967-06-06 | Olin Mathieson | Concentric tube heat exchanger with sintered metal matrix |
US3339260A (en) * | 1964-11-25 | 1967-09-05 | Olin Mathieson | Method of producing heat exchangers |
US3474513A (en) * | 1967-04-07 | 1969-10-28 | William D Allingham | Method of fabricating a cored structure |
US3477503A (en) * | 1967-11-14 | 1969-11-11 | John L Curren | Domestic hot water generator |
US3521707A (en) * | 1967-09-13 | 1970-07-28 | Ass Eng Ltd | Heat exchangers |
US3636607A (en) * | 1969-12-30 | 1972-01-25 | United Aircraft Prod | Method of making a heat exchange tube |
US3705618A (en) * | 1968-12-27 | 1972-12-12 | Etienne Jouet | Heat exchanger |
US3732921A (en) * | 1971-06-30 | 1973-05-15 | Modine Mfg Co | Heat exchanger |
US3823458A (en) * | 1968-12-27 | 1974-07-16 | E Jouet | Method of manufacturing a spirally wound heat exchanger |
US3831247A (en) * | 1971-11-22 | 1974-08-27 | United Aircraft Prod | Method of metallurgically bonding a internally finned heat exchange structure |
US3959867A (en) * | 1974-10-15 | 1976-06-01 | Modine Manufacturing Company | Method of making a heat exchanger and the heat exchanger |
US4031602A (en) * | 1976-04-28 | 1977-06-28 | Uop Inc. | Method of making heat transfer tube |
US4059882A (en) * | 1976-05-24 | 1977-11-29 | United Aircraft Products, Inc. | Method of making an annular tube-fin heat exchanger |
US4063431A (en) * | 1976-08-11 | 1977-12-20 | Gerhard Dankowski | Compact cooling system for automotive vehicles |
US4096616A (en) * | 1976-10-28 | 1978-06-27 | General Electric Company | Method of manufacturing a concentric tube heat exchanger |
US4163474A (en) * | 1976-03-10 | 1979-08-07 | E. I. Du Pont De Nemours And Company | Internally finned tube |
US4190105A (en) * | 1976-08-11 | 1980-02-26 | Gerhard Dankowski | Heat exchange tube |
US4284133A (en) * | 1979-09-19 | 1981-08-18 | Dunham-Bush, Inc. | Concentric tube heat exchange assembly with improved internal fin structure |
US4419802A (en) * | 1980-09-11 | 1983-12-13 | Riese W A | Method of forming a heat exchanger tube |
US4470188A (en) * | 1982-08-31 | 1984-09-11 | The Babcock & Wilcox Company | Method of mechanically prestressing a tubular apparatus |
US4538337A (en) * | 1982-08-31 | 1985-09-03 | The Babcock & Wilcox Company | Method of mechanically prestressing a tubular apparatus |
US4593754A (en) * | 1980-06-24 | 1986-06-10 | Holl Richard A | Shell and tube heat transfer apparatus and process therefor |
US4742866A (en) * | 1985-06-25 | 1988-05-10 | Nippondenso Co., Ltd. | Heat exchanger |
US4798241A (en) * | 1983-04-04 | 1989-01-17 | Modine Manufacturing | Mixed helix turbulator for heat exchangers |
US4817672A (en) * | 1985-02-12 | 1989-04-04 | Jogema Holding B.V. | Composite tube for heating gases |
US4852642A (en) * | 1987-11-06 | 1989-08-01 | Lee Yong N | Heat exchange device |
US5107922A (en) * | 1991-03-01 | 1992-04-28 | Long Manufacturing Ltd. | Optimized offset strip fin for use in contact heat exchangers |
US5167275A (en) * | 1989-12-06 | 1992-12-01 | Stokes Bennie J | Heat exchanger tube with turbulator |
US5209289A (en) * | 1991-12-02 | 1993-05-11 | Robinson Fin Machines, Inc. | Lanced ruffled turbulizer |
US5522453A (en) * | 1995-03-22 | 1996-06-04 | Green; Kenneth E. | Washer fluid heater |
US5732769A (en) * | 1995-03-17 | 1998-03-31 | Behr Gmbh & Co. | Double-pipe heat exchanger and process for manufacturing same |
US5950716A (en) * | 1992-12-15 | 1999-09-14 | Valeo Engine Cooling Ab | Oil cooler |
US6095236A (en) * | 1997-08-19 | 2000-08-01 | Grueter Elektroapparate Ag | Heat exchanger, in particular for a heating and cooling configuration of an extruder barrel |
US6273183B1 (en) * | 1997-08-29 | 2001-08-14 | Long Manufacturing Ltd. | Heat exchanger turbulizers with interrupted convolutions |
US6347453B1 (en) * | 1998-05-22 | 2002-02-19 | Matthew P. Mitchell | Assembly method for concentric foil regenerators |
-
2003
- 2003-08-29 US US10/652,768 patent/US20050045315A1/en not_active Abandoned
- 2003-08-29 CA CA2439023A patent/CA2439023C/fr not_active Expired - Fee Related
Patent Citations (47)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3126918A (en) * | 1964-03-31 | Slip ring spacer for insulated conduit systems | ||
US2468909A (en) * | 1946-01-03 | 1949-05-03 | Cnossen | Auxiliary air heater |
US2703921A (en) * | 1949-04-14 | 1955-03-15 | Brown Fintube Co | Method of making internally finned tubes |
US2693026A (en) * | 1950-02-17 | 1954-11-02 | Modine Mfg Co | Method of making concentric tubes with radial fins |
US2726681A (en) * | 1950-09-18 | 1955-12-13 | Brown Fintube Co | Internally finned tube |
US2731709A (en) * | 1950-09-18 | 1956-01-24 | Brown Fintube Co | Method of making internally finned heat exchanger tubes |
US2712438A (en) * | 1951-04-27 | 1955-07-05 | Brown Fintube Co | Heat exchanger |
US2692763A (en) * | 1952-03-08 | 1954-10-26 | Air Preheater | Supporting spacer for annular corrugated fins |
US2756032A (en) * | 1952-11-17 | 1956-07-24 | Heater | |
US2752128A (en) * | 1955-10-17 | 1956-06-26 | Modine Mfg Co | Heat exchange structure |
US3001767A (en) * | 1959-11-16 | 1961-09-26 | Kenmore Machine Products Inc | Tubular structure |
US3323586A (en) * | 1964-10-14 | 1967-06-06 | Olin Mathieson | Concentric tube heat exchanger with sintered metal matrix |
US3339260A (en) * | 1964-11-25 | 1967-09-05 | Olin Mathieson | Method of producing heat exchangers |
US3474513A (en) * | 1967-04-07 | 1969-10-28 | William D Allingham | Method of fabricating a cored structure |
US3521707A (en) * | 1967-09-13 | 1970-07-28 | Ass Eng Ltd | Heat exchangers |
US3477503A (en) * | 1967-11-14 | 1969-11-11 | John L Curren | Domestic hot water generator |
US3705618A (en) * | 1968-12-27 | 1972-12-12 | Etienne Jouet | Heat exchanger |
US3823458A (en) * | 1968-12-27 | 1974-07-16 | E Jouet | Method of manufacturing a spirally wound heat exchanger |
US3636607A (en) * | 1969-12-30 | 1972-01-25 | United Aircraft Prod | Method of making a heat exchange tube |
US3732921A (en) * | 1971-06-30 | 1973-05-15 | Modine Mfg Co | Heat exchanger |
US3831247A (en) * | 1971-11-22 | 1974-08-27 | United Aircraft Prod | Method of metallurgically bonding a internally finned heat exchange structure |
US3959867A (en) * | 1974-10-15 | 1976-06-01 | Modine Manufacturing Company | Method of making a heat exchanger and the heat exchanger |
US4163474A (en) * | 1976-03-10 | 1979-08-07 | E. I. Du Pont De Nemours And Company | Internally finned tube |
US4031602A (en) * | 1976-04-28 | 1977-06-28 | Uop Inc. | Method of making heat transfer tube |
US4059882A (en) * | 1976-05-24 | 1977-11-29 | United Aircraft Products, Inc. | Method of making an annular tube-fin heat exchanger |
US4063431A (en) * | 1976-08-11 | 1977-12-20 | Gerhard Dankowski | Compact cooling system for automotive vehicles |
US4190105A (en) * | 1976-08-11 | 1980-02-26 | Gerhard Dankowski | Heat exchange tube |
US4096616A (en) * | 1976-10-28 | 1978-06-27 | General Electric Company | Method of manufacturing a concentric tube heat exchanger |
US4284133A (en) * | 1979-09-19 | 1981-08-18 | Dunham-Bush, Inc. | Concentric tube heat exchange assembly with improved internal fin structure |
US4593754A (en) * | 1980-06-24 | 1986-06-10 | Holl Richard A | Shell and tube heat transfer apparatus and process therefor |
US4419802A (en) * | 1980-09-11 | 1983-12-13 | Riese W A | Method of forming a heat exchanger tube |
US4470188A (en) * | 1982-08-31 | 1984-09-11 | The Babcock & Wilcox Company | Method of mechanically prestressing a tubular apparatus |
US4538337A (en) * | 1982-08-31 | 1985-09-03 | The Babcock & Wilcox Company | Method of mechanically prestressing a tubular apparatus |
US4798241A (en) * | 1983-04-04 | 1989-01-17 | Modine Manufacturing | Mixed helix turbulator for heat exchangers |
US4817672A (en) * | 1985-02-12 | 1989-04-04 | Jogema Holding B.V. | Composite tube for heating gases |
US4742866A (en) * | 1985-06-25 | 1988-05-10 | Nippondenso Co., Ltd. | Heat exchanger |
US4852642A (en) * | 1987-11-06 | 1989-08-01 | Lee Yong N | Heat exchange device |
US5167275A (en) * | 1989-12-06 | 1992-12-01 | Stokes Bennie J | Heat exchanger tube with turbulator |
USRE35890E (en) * | 1991-03-01 | 1998-09-08 | Long Manufacturing Ltd. | Optimized offset strip fin for use in compact heat exchangers |
US5107922A (en) * | 1991-03-01 | 1992-04-28 | Long Manufacturing Ltd. | Optimized offset strip fin for use in contact heat exchangers |
US5209289A (en) * | 1991-12-02 | 1993-05-11 | Robinson Fin Machines, Inc. | Lanced ruffled turbulizer |
US5950716A (en) * | 1992-12-15 | 1999-09-14 | Valeo Engine Cooling Ab | Oil cooler |
US5732769A (en) * | 1995-03-17 | 1998-03-31 | Behr Gmbh & Co. | Double-pipe heat exchanger and process for manufacturing same |
US5522453A (en) * | 1995-03-22 | 1996-06-04 | Green; Kenneth E. | Washer fluid heater |
US6095236A (en) * | 1997-08-19 | 2000-08-01 | Grueter Elektroapparate Ag | Heat exchanger, in particular for a heating and cooling configuration of an extruder barrel |
US6273183B1 (en) * | 1997-08-29 | 2001-08-14 | Long Manufacturing Ltd. | Heat exchanger turbulizers with interrupted convolutions |
US6347453B1 (en) * | 1998-05-22 | 2002-02-19 | Matthew P. Mitchell | Assembly method for concentric foil regenerators |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9459052B2 (en) | 2011-03-01 | 2016-10-04 | Dana Canada Corporation | Coaxial gas-liquid heat exchanger with thermal expansion connector |
US11029095B2 (en) * | 2015-07-30 | 2021-06-08 | Senior Uk Limited | Finned coaxial cooler |
CN112005071A (zh) * | 2018-04-24 | 2020-11-27 | G·玛南蒂 | 双管热交换器及其制造方法 |
US11668529B2 (en) | 2018-04-24 | 2023-06-06 | Giovanni MANENTI | Double-tube heat exchanger and manufacturing method thereof |
Also Published As
Publication number | Publication date |
---|---|
CA2439023A1 (fr) | 2005-02-28 |
CA2439023C (fr) | 2011-12-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US5697433A (en) | Heat-exchanger conduit for tube-stacking type heat exchanger and method of manufacturing it | |
US20050155748A1 (en) | Concentric tube heat exchanger end seal therefor | |
US5025855A (en) | Condenser for use in a car cooling system | |
US5996633A (en) | Heat-exchanging conduit tubes for laminated heat exchanger and method for producing same | |
US6173493B1 (en) | Modular heat exchanger and method of making | |
US5295302A (en) | Method of manufacturing an aluminum heat exchanger | |
JPS62207572A (ja) | 熱交換器の作製方法 | |
JPH0599584A (ja) | 平行流式熱交換器用のマニホールド組立体 | |
US6513582B2 (en) | Heat exchanger and fluid pipe therefor | |
US5732769A (en) | Double-pipe heat exchanger and process for manufacturing same | |
MXPA05005637A (es) | Tubo resistente de ciclacion termica para junta de cabezal para intercambiadores de calor. | |
WO2004083745A1 (fr) | Échangeur de chaleur | |
US20070000652A1 (en) | Heat exchanger with dimpled tube surfaces | |
JP4926972B2 (ja) | プロファイル圧延した金属製品から製造された管およびその製造方法 | |
US4509672A (en) | Method of constructing headers of heat exchangers | |
CA2682620A1 (fr) | Structure d'echangeur thermique | |
JP2000346584A (ja) | 熱交換器 | |
CA2439023C (fr) | Echangeur de chaleur a tubes concentriques et embout d'etancheite connexe | |
US4381033A (en) | Header construction | |
CN100520267C (zh) | 用于换热器的管型面 | |
EP1023568B1 (fr) | Echangeur de chaleur modulaire et son procede de fabrication | |
JPH0474099B2 (fr) | ||
US20070284086A1 (en) | Transition assembly and method of connecting to a heat exchanger | |
CA1130790A (fr) | Echangeur de chaleur | |
AU2003244027A1 (en) | Concentric tube heat exchanger and end seal therefor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: DANA CANADA CORPORATION, CANADA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SEAGER, JAMES R.;KO, ALLAN K.;BROWN, ALAN S.;AND OTHERS;REEL/FRAME:014925/0600;SIGNING DATES FROM 20031215 TO 20040120 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |