US20050045315A1 - Concentric tube heat exchanger and end seal therefor - Google Patents
Concentric tube heat exchanger and end seal therefor Download PDFInfo
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- 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
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- heat exchanger
- sealing member
- walls
- tubes
- sealing
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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
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.
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 an inlet fitting 26 and an outlet fitting 28 which are mounted to the outer surface of theouter tube 12 in communication with the inlet andoutlet ports fittings outer tube 12, the areas surrounding inlet andoutlet ports FIG. 6 . Sealed connections are formed betweenfittings 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 sealingmember 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. A concentric tube heat exchanger having a first end and a second end, the heat exchanger comprising:
(a) an outer tube;
(b) an inner tube received inside the outer tube and concentric therewith, wherein an annular passageway is formed between the inner and outer tubes;
(c) first and second annular sealing members received inside the annular passageway between the inner and outer tubes, the first sealing member being positioned proximate the first end of the heat exchanger and the second sealing member being positioned proximate the second end of the heat exchanger, each of the sealing members comprising 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.
2. The concentric tube heat exchanger of claim 1 , wherein each of the sealing member walls has an axially-extending portion between its first and second end.
3. The concentric tube heat exchanger of claim 1 , wherein the inner and outer walls of the sealing members are connected through a connecting portion which seals a radial space between the sealing member walls.
4. The concentric tube heat exchanger of claim 3; wherein the sealing members are 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.
5. The concentric tube heat exchanger of claim 1 , wherein the sealing members are spaced inward from the ends of the heat exchanger, such that the second ends of the sealing member walls are proximate to, and spaced inwardly from, the ends of the heat exchanger.
6. The concentric tube heat exchanger of claim 5 , wherein the sealing members are brazed to the tubes such that fillets of filler metal are formed between the tubes and the ends of the sealing member walls, and wherein the sealing members are spaced inwardly from the ends of the heat exchanger by a distance sufficient that the fillets between the second ends of the sealing member walls and the tubes are located inwardly of the ends of the heat exchanger.
7. The concentric tube heat exchanger of claim 3 , wherein the connecting portion is rounded.
8. The concentric tube heat exchanger of claim 3 , wherein the connecting portion is flat.
9. The concentric tube heat exchanger of claim 1 , wherein the tubes and the sealing members are comprised of aluminum.
10. The concentric tube heat exchanger of claim 9 , wherein the tubes are provided with a cladding comprised of a brazing alloy, at least on surfaces which are joined to the sealing members.
11. The concentric tube heat exchanger of claim 10 , wherein the sealing members are provided with a cladding comprised of a brazing alloy, at least one surfaces which are joined to the tubes.
12. The concentric tube heat exchanger of claim 1 , further comprising a turbulizer received in the annular passageway, the turbulizer comprising a plurality of corrugations defining a plurality of axially extending flow passages extending parallel to the tubes, each of the corrugations comprising 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;
wherein 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 having a width which is from about 30 percent to about 40 percent of a width of the top land or the bottom land.
13. The concentric tube heat exchanger of claim 12 , wherein the width of the offset is from about 31 percent to about 36 percent of the top land width or the bottom land width.
14. The concentric tube heat exchanger of claim 13 , wherein the width of the offset is about 31 percent of the top land width.
15. The concentric tube heat exchanger of claim 13 , wherein the width of the offset is about 36 percent of the bottom land width.
16. The concentric tube heat exchanger of claim 13 , wherein the top land width is greater than the bottom land width and wherein the side surfaces extend radially between the inner and outer tubes.
17. The concentric tube heat exchanger of claim 13 , wherein the tubes and the turbulizer are comprised of aluminum with the top land being brazed to the outer tube and the bottom land being brazed to the inner tube.
18. 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 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, the generally axially-extending portions of the sealing member walls extend between the connecting portion and the second end, and wherein the generally axially-extending portions diverge from said connecting portion to the second ends of 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, during assembly, the sealing members are slidably received in the annular passageway 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.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA2439023A CA2439023C (en) | 2003-08-29 | 2003-08-29 | Concentric tube heat exchanger and end seal therefor |
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 (en) | 2003-08-29 | 2003-08-29 | Concentric tube heat exchanger and end seal therefor |
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 |
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US (1) | US20050045315A1 (en) |
CA (1) | CA2439023C (en) |
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 (en) * | 2018-04-24 | 2020-11-27 | G·玛南蒂 | Double-tube heat exchanger and method for manufacturing same |
US11029095B2 (en) * | 2015-07-30 | 2021-06-08 | Senior Uk Limited | Finned coaxial cooler |
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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 (en) * | 2018-04-24 | 2020-11-27 | G·玛南蒂 | Double-tube heat exchanger and method for manufacturing same |
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 (en) | 2005-02-28 |
CA2439023C (en) | 2011-12-06 |
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