US20090159253A1 - Heat exchanger tubes and combo-coolers including the same - Google Patents
Heat exchanger tubes and combo-coolers including the same Download PDFInfo
- Publication number
- US20090159253A1 US20090159253A1 US11/963,131 US96313107A US2009159253A1 US 20090159253 A1 US20090159253 A1 US 20090159253A1 US 96313107 A US96313107 A US 96313107A US 2009159253 A1 US2009159253 A1 US 2009159253A1
- Authority
- US
- United States
- Prior art keywords
- flow passages
- thickness
- heat exchanger
- opposed sides
- wall
- 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
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
- F28D1/0443—Combination of units extending one beside or one above the other
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/14—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by endowing the walls of conduits with zones of different degrees of conduction of heat
Definitions
- the present disclosure relates generally to heat exchanger tubes, and to combo-coolers including such heat exchanger tubes.
- Two goals for heat exchanger manufacturing often include forming a product that exhibits efficient transfer of heat, while maintaining a relatively simple manufacturing process.
- Combo-coolers are an example of such an assembly and include multiple coolers.
- the tubes of each cooler are connected to the same pair of manifolds.
- Oil coolers have been added to automotive combo-coolers. Such oil coolers often have a tube and fin structure, in part because of cost efficiency and ease of assembly.
- FIG. 1 is a schematic view of an embodiment of a heat exchanger assembly
- FIG. 2 is a schematic cross-sectional view of an embodiment of a heat exchanger tube
- FIG. 3 is a schematic cross-sectional view of another embodiment of a heat exchanger tube
- FIG. 4 is a schematic cross-sectional cut-away view of still another embodiment of a heat exchanger tube.
- FIG. 5 is a schematic cross-sectional view of still another embodiment of a heat exchanger tube.
- Embodiments of the heat exchanger tubes disclosed herein advantageously include multiple flow passages, and a varying wall thickness. It is believed that the varying wall thickness decreases thermal stress and improves thermal performance.
- the inclusion of a standard oil cooler into a combo-cooler may increase thermal stress. This may be due, at least in part, to the fact that the tubes of the oil cooler and the tubes of the other coolers (e.g., the condenser) do not expand by the same amount (e.g., length), but are connected to the same manifold.
- the coefficient of thermal expansion is the same; however, due to the different temperatures, the thermal expansion of the tubes is different.
- the manifold may exert compression on the oil cooler tube and tension on condenser tube.
- the present inventors have analyzed failure modes of oil cooler tubes using thermal cycle tests.
- the tests indicate that the weakest tube is generally the oil cooler tube positioned closest to the condenser.
- the tests also indicated that the oil cooler tubes were susceptible to the formation of micro-cracks, especially at a center of the tube.
- the micro-cracks would form at the center, and extend, in general, to the sides of the tubes.
- the term “center of the tube” generally refers to the middle area of the tube when viewing a cross-section of a substantially flat tube, see, for example FIGS. 2 through 5 .
- the term “sides of the tube” generally refers to those areas adjacent the opposite ends of the width of the tube when viewing a cross-section of a substantially flat tube.
- the present inventors believe that by varying the thickness of the tube walls, and by increasing the thickness near the center, the formation of micro-cracks is substantially delayed or eliminated, thereby extending the life and performance of the tube. It is also believed that the varying thickness enhances the durability of the tube for withstanding thermal stress, thereby enabling additional flow passages to be formed in the tubes.
- Such an assembly 100 generally includes first and second end tanks or manifolds 110 , 110 ′, a plurality of tubes 10 , 10 ′, 10 ′′, 10 ′′′ extending between the end tanks 110 , 110 ′, and fins 112 separating each of the plurality of tubes 10 , 10 ′, 10 ′′, 10 ′′′.
- Each plurality of tubes 10 , 10 ′, 10 ′′, 10 ′′′ may range from about 100 mm to about 1000 mm in length (i.e., from one end tank 110 to the other 110 ′).
- each of the end tanks 110 , 110 ′ generally includes an inlet 114 , an outlet 116 and baffles 118 , 118 ′.
- baffles 118 in each of the end tanks 110 , 110 ′ separate the respective heat exchangers HE 1 , HE 2 from each other. It is to be understood that additional baffles 118 ′ may be positioned within one or both end tanks 110 , 110 ′ to direct the flow of fluid within a particular heat exchanger HE 1 , HE 2 .
- one or more of the tubes 10 , 10 ′, 10 ′′, 10 ′′′ in the combo-cooler 100 includes flow passages (shown in FIGS. 2 through 5 ) and a tube body wall having a varying wall thickness.
- Such tubes 10 , 10 ′, 10 ′′, 10 ′′′ are described in more detail in reference to these other figures.
- FIG. 1 While a combo-cooler 100 is shown in FIG. 1 , it is to be understood that the tubes 10 , 10 ′, 10 ′′, 10 ′′′ disclosed herein may be implemented into a single heat exchanger (not shown).
- FIG. 2 depicts a cross-section of one embodiment of such a tube 10 .
- the tube 10 includes a tube body 12 , and a plurality of flow passages 14 defined in the tube body 12 . As depicted, each of the flow passages 14 is fluidly separated from each of the other flow passages 14 via a web 16 . It is to be understood that the web(s) 16 may be formed integrally with the tube body 12 , or may be securely attached to the tube body 12 .
- the tube body 12 and the web(s) 16 may be formed of any suitable material or alloys thereof, including copper, copper alloys, aluminum, or aluminum alloys.
- Examples of processes that may be used to form the tube 10 , flow passages 14 , and webs 16 include, but are not limited to extrusion, roll-forming, or bending and brazing.
- the tube body 12 shown in FIG. 2 is substantially oblong. However, it is to be understood that the tube body 12 may have any desirable configuration. In some instances, an oval shaped tube body 12 may be desirable (see, for example, FIG. 3 ).
- the tube body 12 also includes a wall 18 having a thickness (e.g., T 1 , T 2 , etc.) which varies over a width W T of the tube body 12 .
- the width W T also known as core depth
- the width W T of the tube body 12 ranges from about 8 mm to about 70 mm.
- the width W T of the tube body 12 extends from one side S 1 to an opposed side S 2 .
- the wall 18 thickness may vary across the width W T as is desired, however, as previously described, it may be particularly advantageous to form the thickest portion (see, e.g., thickness T 4 ) at or near a center C of the tube body 12 .
- the thickness may vary gradually across the entire width W T (as shown in FIG. 2 ), or it may be consistent for a predetermined portion and then vary (as shown and discussed further in reference to FIG. 3 ). Generally, the varying thickness ranges from about 0.1 mm to about 0.9 mm.
- the wall 18 thickness (see, e.g., T 4 ) at or near the center C of the tube body 12 ranges from about 0.3 mm to about 0.9 mm, and the wall 18 thickness (see, e.g., T 1 ) at or near each of the opposed sides S 1 , S 2 ranges from about 0.1 mm to about 0.6 mm.
- the wall 18 thickness is substantially symmetrical from the center C to each of the two opposed sides S 1 , S 2 .
- the thickness increases along the width W T extending from each of the two opposed sides S 1 , S 2 toward the center C, and as such, it decreases along the width W T extending from the center C toward each of the two opposed sides S 1 , S 2 .
- the wall 18 thickness T 4 is greatest at or near the center C, and the wall thickness T 1 is smallest at or near each of the opposed sides S 1 , S 2 .
- the thicknesses T 2 , T 3 are between the greatest thickness T 4 and the smallest thickness T 1 .
- the thickness of the wall 18 varies along the entire width W T of the tube body 12 , the thickness also varies along the width W FP of each individual flow passage 14 . As shown in FIG. 2 , the varying wall 18 thickness affects the cross sectional area of the respective flow passages 14 . Generally, when the thickness increases, the area decreases. As such, in the embodiment shown in FIG. 2 , the cross sectional area of the flow passages 14 closer to the two opposed sides S 1 , S 2 is larger than the cross sectional area of the flow passages 14 closer to the center C.
- the thickness along the width W T is not symmetrical, rather it increases extending from each of the two opposed sides S 1 , S 2 toward some other predetermined point (i.e., other than the center C). In such embodiments, the thickness is asymmetrical.
- the wall 18 has at least three portions P 1 , P 2 , P 3 .
- the thickness of the wall 18 remains substantially consistent, but from one portion P 1 , P 2 , P 3 to another portion P 1 , P 2 , P 3 , the thickness of the wall 18 changes.
- the thickness of the wall 18 is consistent at some point(s) along the width W T of the tube body 12 , and varies at other point(s) along the width W T of the tube body 12 .
- the portions P 1 , P 2 , P 3 substantially align with a width W FP of a respective flow passage 14 . It is to be understood that the portions P 1 , P 2 , P 3 may extend beyond the width W FP of the flow passages 14 (as shown in FIG. 3 ), depending at least in part, on where along the width W T of the tube body 12 it is desirable to vary the thickness. As such, in some embodiments, a consistent wall 18 thickness is adjacent at least one particular flow passage 14 .
- the thickness T 2 is consistent along portion P 1 , which includes the entire width W FP of the flow passage 14 directly adjacent thereto, and the thickness T 3 is consistent along portion P 2 , which includes the entire width W FP of the flow passage 14 directly adjacent thereto. As depicted, the thickness T 2 is different from the thickness T 3 . In other instances, it may be desirable to extend a particular thickness (e.g., T 1 , T 2 , T 3 , T 4 ) along two or more adjacent flow passages 14 .
- a particular thickness e.g., T 1 , T 2 , T 3 , T 4
- FIG. 3 again depicts that the thickness is substantially symmetrical from the center C towards the two opposed sides S 1 , S 2 .
- the thickness may vary as desired. Also as previously described, it may be particularly suitable to have the thickest wall 18 at or near the center C of the tube body 12 (even when the thickness is not symmetrical).
- the portions P 1 , P 2 , P 3 do not have to be aligned with the respective flow passages 14 , and may be configured as is desirable for a particular end use.
- the thickness T 4 at the center C may be substantially consistent along the width W FP of the flow passage 14 directly adjacent thereto, while the rest of the wall 18 thickness T 3 , T 2 , T 1 may gradually vary along the remainder of the width W T of the tube body 12 (e.g., as shown in FIG. 2 ).
- FIG. 4 depicts cross-sectional view of still another embodiment of the tube 10 ′′.
- micro-fins 20 are established on the wall 18 , the web(s) 16 and/or combinations thereof. It is to be understood that the micro-fins 20 are formed such that they protrude into an interior of the flow passage(s) 14 .
- the micro-fins 20 may be formed integrally with the wall 18 and/or web 16 . It is believed that the micro-fins 20 further enhance the thermal performance of the tube 10 ′′.
- FIG. 5 another cross-section of another embodiment of the tube 10 ′′′ is depicted.
- the configuration of the flow passages 14 alters the thickness of the wall 18 .
- at least some of the flow passages 14 have a first configuration C 1 (e.g., oval), and at least some other of the flow passages 14 have a second configuration C 2 (e.g., rectangular) that is different than the first configuration C 1 .
- any suitable configurations C 1 , C 2 may be used, as long as at least a portion of the thickness T 1 of the wall 18 adjacent the flow passages 14 having first configuration C 1 is different from at least a portion of the thickness T 2 of the wall 18 adjacent the flow passages 14 having the second configuration C 2 .
- the flow passages 14 at or near the center C of the tube body 12 have a configuration C 2 which results in at least a portion of the wall thickness T 2 adjacent thereto being greater.
- the average wall thickness T 2 is larger than the average wall thickness T 1 , at least in part, because of the special (e.g., rounded) shape of the ends of the flow passages 14 having configuration C 1 compared with the flat ends of the flow passages of the configuration C 2 .
- micro-fins 20 are also shown formed integrally with the webs 16 such that they protrude into an interior of the flow passage(s) 14 . As previously stated, it is believed that the micro-fins 20 further enhance the thermal performance of the tube 10 ′′′.
- a combo-cooler with 22 mm ⁇ 4 mm tubes, each including 13 flow passages was formed. This combo-cooler has a varying thickness between the sides, and the thickness averaged 0.45 mm. The combo-cooler was exposed to thermal cycles until failure.
- a comparative combo-cooler with 22 mm ⁇ 4 mm tubes, each including 12 flow passages and a uniform wall thickness (0.45 mm along the tube width) was also tested. The results are shown in Table 1 below.
- the varying wall thickness substantially enhances the life and efficiency of the tubes. Additional flow passages generally decrease tube resistance to thermal cycles. As such, it was expected that the combo-cooler including more flow passages would have failed prior to the combo-cooler having less flow passages. The results indicate that varying the wall thickness increases the durability of the tubes, thereby allowing additional flow passages to be formed therein and improving the thermal cycle performance.
- Embodiments of the heat exchanger tubes 10 , 10 ′, 10 ′′ disclosed herein advantageously include a varying wall 18 thickness. It is believed that the varying wall 18 thickness, delays, decreases or eliminates the formation of micro-cracks at thicker areas, and reduces the amount of material used at thinner areas. It is also believed that the varying thickness also advantageously enhances the durability of the tube 10 , 10 ′, 10 ′′ for withstanding thermal stress, and enhances the overall efficiency of the combo-cooler 100 .
Abstract
A heat exchanger tube includes a tube body and a plurality of flow passages defined therein. The tube body includes two opposed sides, and a wall having a thickness that varies between the two opposed sides.
Description
- The present disclosure relates generally to heat exchanger tubes, and to combo-coolers including such heat exchanger tubes.
- Two goals for heat exchanger manufacturing often include forming a product that exhibits efficient transfer of heat, while maintaining a relatively simple manufacturing process. In the automotive industry, in particular, it has also become desirable to combine multiple functions into a single heat exchanger assembly. Combo-coolers are an example of such an assembly and include multiple coolers. In a combo-cooler, the tubes of each cooler are connected to the same pair of manifolds. Oil coolers have been added to automotive combo-coolers. Such oil coolers often have a tube and fin structure, in part because of cost efficiency and ease of assembly.
- Features and advantages of embodiments of the present disclosure will become apparent by reference to the following detailed description and drawings, in which like reference numerals correspond to the same or similar, though perhaps not identical, components. For the sake of brevity, reference numerals having a previously described function may or may not be described in connection with subsequent drawings in which they appear.
-
FIG. 1 is a schematic view of an embodiment of a heat exchanger assembly; -
FIG. 2 is a schematic cross-sectional view of an embodiment of a heat exchanger tube; -
FIG. 3 is a schematic cross-sectional view of another embodiment of a heat exchanger tube; -
FIG. 4 is a schematic cross-sectional cut-away view of still another embodiment of a heat exchanger tube; and -
FIG. 5 is a schematic cross-sectional view of still another embodiment of a heat exchanger tube. - Embodiments of the heat exchanger tubes disclosed herein advantageously include multiple flow passages, and a varying wall thickness. It is believed that the varying wall thickness decreases thermal stress and improves thermal performance.
- The inclusion of a standard oil cooler into a combo-cooler may increase thermal stress. This may be due, at least in part, to the fact that the tubes of the oil cooler and the tubes of the other coolers (e.g., the condenser) do not expand by the same amount (e.g., length), but are connected to the same manifold. The coefficient of thermal expansion is the same; however, due to the different temperatures, the thermal expansion of the tubes is different. For example, when hot oil flows inside the oil cooler, oil cooler tubes tend to expand, while at the same time, the condenser tube may be cooler, and thus not expand as much. In this case, the manifold may exert compression on the oil cooler tube and tension on condenser tube.
- The present inventors have analyzed failure modes of oil cooler tubes using thermal cycle tests. The tests indicate that the weakest tube is generally the oil cooler tube positioned closest to the condenser. The tests also indicated that the oil cooler tubes were susceptible to the formation of micro-cracks, especially at a center of the tube. The micro-cracks would form at the center, and extend, in general, to the sides of the tubes. As used herein, the term “center of the tube” generally refers to the middle area of the tube when viewing a cross-section of a substantially flat tube, see, for example
FIGS. 2 through 5 . Also as used herein, the term “sides of the tube” generally refers to those areas adjacent the opposite ends of the width of the tube when viewing a cross-section of a substantially flat tube. - Without being bound to any theory, the present inventors believe that by varying the thickness of the tube walls, and by increasing the thickness near the center, the formation of micro-cracks is substantially delayed or eliminated, thereby extending the life and performance of the tube. It is also believed that the varying thickness enhances the durability of the tube for withstanding thermal stress, thereby enabling additional flow passages to be formed in the tubes.
- Referring now to
FIG. 1 , an embodiment of a heat exchanger assembly or combo-cooler 100 is depicted. Such anassembly 100 generally includes first and second end tanks ormanifolds tubes end tanks fins 112 separating each of the plurality oftubes tubes end tank 110 to the other 110′). As shown inFIG. 1 , each of theend tanks inlet 114, anoutlet 116 andbaffles - One of the
inlets 114 and one of theoutlets 116 service a first heat exchanger HE1, and another of theinlets 114 and another of theoutlets 116 service a second heat exchanger HE2.Baffles 118 in each of theend tanks additional baffles 118′ may be positioned within one or bothend tanks - It is to be understood that one or more of the
tubes cooler 100 includes flow passages (shown inFIGS. 2 through 5 ) and a tube body wall having a varying wall thickness.Such tubes - While a combo-
cooler 100 is shown inFIG. 1 , it is to be understood that thetubes -
FIG. 2 depicts a cross-section of one embodiment of such atube 10. Generally, thetube 10 includes atube body 12, and a plurality offlow passages 14 defined in thetube body 12. As depicted, each of theflow passages 14 is fluidly separated from each of theother flow passages 14 via aweb 16. It is to be understood that the web(s) 16 may be formed integrally with thetube body 12, or may be securely attached to thetube body 12. Thetube body 12 and the web(s) 16 may be formed of any suitable material or alloys thereof, including copper, copper alloys, aluminum, or aluminum alloys. - Examples of processes that may be used to form the
tube 10,flow passages 14, andwebs 16 include, but are not limited to extrusion, roll-forming, or bending and brazing. - The
tube body 12 shown inFIG. 2 is substantially oblong. However, it is to be understood that thetube body 12 may have any desirable configuration. In some instances, an ovalshaped tube body 12 may be desirable (see, for example,FIG. 3 ). - The
tube body 12 also includes awall 18 having a thickness (e.g., T1, T2, etc.) which varies over a width WT of thetube body 12. In one embodiment, the width WT (also known as core depth) of thetube body 12 ranges from about 8 mm to about 70 mm. Generally, the width WT of thetube body 12 extends from one side S1 to an opposed side S2. It is to be understood that thewall 18 thickness may vary across the width WT as is desired, however, as previously described, it may be particularly advantageous to form the thickest portion (see, e.g., thickness T4) at or near a center C of thetube body 12. - The thickness may vary gradually across the entire width WT (as shown in
FIG. 2 ), or it may be consistent for a predetermined portion and then vary (as shown and discussed further in reference toFIG. 3 ). Generally, the varying thickness ranges from about 0.1 mm to about 0.9 mm. In an embodiment, thewall 18 thickness (see, e.g., T4) at or near the center C of thetube body 12 ranges from about 0.3 mm to about 0.9 mm, and thewall 18 thickness (see, e.g., T1) at or near each of the opposed sides S1, S2 ranges from about 0.1 mm to about 0.6 mm. - In the embodiment shown in
FIG. 2 , thewall 18 thickness is substantially symmetrical from the center C to each of the two opposed sides S1, S2. The thickness increases along the width WT extending from each of the two opposed sides S1, S2 toward the center C, and as such, it decreases along the width WT extending from the center C toward each of the two opposed sides S1, S2. In this embodiment, thewall 18 thickness T4 is greatest at or near the center C, and the wall thickness T1 is smallest at or near each of the opposed sides S1, S2. As shown inFIG. 2 , between the center C and each of the two opposed sides, the thicknesses T2, T3 are between the greatest thickness T4 and the smallest thickness T1. - Since the thickness of the
wall 18 varies along the entire width WT of thetube body 12, the thickness also varies along the width WFP of eachindividual flow passage 14. As shown inFIG. 2 , thevarying wall 18 thickness affects the cross sectional area of therespective flow passages 14. Generally, when the thickness increases, the area decreases. As such, in the embodiment shown inFIG. 2 , the cross sectional area of theflow passages 14 closer to the two opposed sides S1, S2 is larger than the cross sectional area of theflow passages 14 closer to the center C. - It is to be understood that in other instances (not shown in the Figures), the thickness along the width WT is not symmetrical, rather it increases extending from each of the two opposed sides S1, S2 toward some other predetermined point (i.e., other than the center C). In such embodiments, the thickness is asymmetrical.
- Referring now to
FIG. 3 , a cross-section of another embodiment of thetube 10′ is depicted. In this embodiment, thewall 18 has at least three portions P1, P2, P3. Along a particular portion P1, P2, P3, the thickness of thewall 18 remains substantially consistent, but from one portion P1, P2, P3 to another portion P1, P2, P3, the thickness of thewall 18 changes. As such, the thickness of thewall 18 is consistent at some point(s) along the width WT of thetube body 12, and varies at other point(s) along the width WT of thetube body 12. - In the embodiment shown in
FIG. 3 , the portions P1, P2, P3 substantially align with a width WFP of arespective flow passage 14. It is to be understood that the portions P1, P2, P3 may extend beyond the width WFP of the flow passages 14 (as shown inFIG. 3 ), depending at least in part, on where along the width WT of thetube body 12 it is desirable to vary the thickness. As such, in some embodiments, aconsistent wall 18 thickness is adjacent at least oneparticular flow passage 14. For example, the thickness T2 is consistent along portion P1, which includes the entire width WFP of theflow passage 14 directly adjacent thereto, and the thickness T3 is consistent along portion P2, which includes the entire width WFP of theflow passage 14 directly adjacent thereto. As depicted, the thickness T2 is different from the thickness T3. In other instances, it may be desirable to extend a particular thickness (e.g., T1, T2, T3, T4) along two or moreadjacent flow passages 14. -
FIG. 3 again depicts that the thickness is substantially symmetrical from the center C towards the two opposed sides S1, S2. As previously described, it is to be understood that the thickness may vary as desired. Also as previously described, it may be particularly suitable to have thethickest wall 18 at or near the center C of the tube body 12 (even when the thickness is not symmetrical). - Still further, it is to be understood that the portions P1, P2, P3 do not have to be aligned with the
respective flow passages 14, and may be configured as is desirable for a particular end use. For example, the thickness T4 at the center C may be substantially consistent along the width WFP of theflow passage 14 directly adjacent thereto, while the rest of thewall 18 thickness T3, T2, T1 may gradually vary along the remainder of the width WT of the tube body 12 (e.g., as shown inFIG. 2 ). -
FIG. 4 depicts cross-sectional view of still another embodiment of thetube 10″. In this embodiment, micro-fins 20 are established on thewall 18, the web(s) 16 and/or combinations thereof. It is to be understood that the micro-fins 20 are formed such that they protrude into an interior of the flow passage(s) 14. The micro-fins 20 may be formed integrally with thewall 18 and/orweb 16. It is believed that the micro-fins 20 further enhance the thermal performance of thetube 10″. - Referring now to
FIG. 5 , another cross-section of another embodiment of thetube 10′″ is depicted. In this embodiment, the configuration of theflow passages 14 alters the thickness of thewall 18. As shown, at least some of theflow passages 14 have a first configuration C1 (e.g., oval), and at least some other of theflow passages 14 have a second configuration C2 (e.g., rectangular) that is different than the first configuration C1. Generally, any suitable configurations C1, C2 may be used, as long as at least a portion of the thickness T1 of thewall 18 adjacent theflow passages 14 having first configuration C1 is different from at least a portion of the thickness T2 of thewall 18 adjacent theflow passages 14 having the second configuration C2. In this embodiment, theflow passages 14 at or near the center C of thetube body 12 have a configuration C2 which results in at least a portion of the wall thickness T2 adjacent thereto being greater. In this embodiment, the average wall thickness T2 is larger than the average wall thickness T1, at least in part, because of the special (e.g., rounded) shape of the ends of theflow passages 14 having configuration C1 compared with the flat ends of the flow passages of the configuration C2. - In
FIG. 5 , micro-fins 20 are also shown formed integrally with thewebs 16 such that they protrude into an interior of the flow passage(s) 14. As previously stated, it is believed that the micro-fins 20 further enhance the thermal performance of thetube 10′″. - To further illustrate the embodiment(s) of the present disclosure, an example is given herein. It is to be understood that this example is provided for illustrative purposes and is not to be construed as limiting the scope of the disclosed embodiment(s).
- A combo-cooler with 22 mm×4 mm tubes, each including 13 flow passages was formed. This combo-cooler has a varying thickness between the sides, and the thickness averaged 0.45 mm. The combo-cooler was exposed to thermal cycles until failure. A comparative combo-cooler with 22 mm×4 mm tubes, each including 12 flow passages and a uniform wall thickness (0.45 mm along the tube width) was also tested. The results are shown in Table 1 below.
-
TABLE 1 Comparative Combo- Combo-Cooler Having Cooler Having Uniform Variable Thickness and Thickness and 12 Flow 13 Flow Passages Passages Number of Thermal 10630 10390 Cycles until Failure - The results clearly indicate that the varying wall thickness substantially enhances the life and efficiency of the tubes. Additional flow passages generally decrease tube resistance to thermal cycles. As such, it was expected that the combo-cooler including more flow passages would have failed prior to the combo-cooler having less flow passages. The results indicate that varying the wall thickness increases the durability of the tubes, thereby allowing additional flow passages to be formed therein and improving the thermal cycle performance.
- Embodiments of the
heat exchanger tubes wall 18 thickness. It is believed that the varyingwall 18 thickness, delays, decreases or eliminates the formation of micro-cracks at thicker areas, and reduces the amount of material used at thinner areas. It is also believed that the varying thickness also advantageously enhances the durability of thetube cooler 100. - While several embodiments have been described in detail, it will be apparent to those skilled in the art that the disclosed embodiments may be modified. Therefore, the foregoing description is to be considered exemplary rather than limiting.
Claims (25)
1. A heat exchanger tube, comprising:
a tube body, including:
two opposed sides; and
a wall having a thickness that varies between the two opposed sides; and
a plurality of flow passages defined in the tube body.
2. The heat exchanger tube as defined in claim 1 wherein the tube body has a width measured from one of the two opposed sides to an other of the two opposed sides, and wherein the wall thickness increases along the width extending from each of the two opposed sides toward a predetermined distance from each of the two opposed sides.
3. The heat exchanger tube as defined in claim 2 wherein an area of the flow passages decreases as the wall thickness increases.
4. The heat exchanger tube as defined in claim 1 wherein the wall thickness is greatest at or near a center of the tube body between the two opposed sides.
5. The heat exchanger tube as defined in claim 4 wherein the wall thickness decreases extending from the center to each of the two opposed sides.
6. The heat exchanger tube as defined in claim 5 wherein the wall thickness at the center of tube body ranges from about 0.3 mm to about 0.9 mm, and wherein the wall thickness at each of the two opposed sides ranges from about 0.1 mm to about 0.6 mm.
7. The heat exchanger tube as defined in claim 5 wherein the wall thickness is symmetric from the center to each of the two opposed sides.
8. The heat exchanger tube as defined in claim 1 wherein the wall thickness is consistent adjacent respective flow passages, and varies from at least one of the plurality of flow passages to another of the plurality of flow passages.
9. The heat exchanger tube as defined in claim 1 , further comprising a web formed of the tube body that fluidly separates each of the plurality of flow passages.
10. The heat exchanger tube as defined in claim 9 , further comprising micro-fins established on the wall, the web or combinations thereof, such that the micro-fins extend into at least one of the plurality of flow passages.
11. The heat exchanger tube as defined in claim 1 wherein the tube body has a substantially oval or oblong shape.
12. The heat exchanger tube as defined in claim 1 wherein the varying wall thickness ranges from about 0.1 mm to about 0.9 mm.
13. The heat exchanger tube as defined in claim 1 wherein the wall has at least two portions, wherein a first of the at least two portions has a first uniform thickness, and wherein a second of the at least two portions has a second uniform thickness that is different from the first uniform thickness.
14. The heat exchanger tube as defined in claim 1 wherein at least some of the plurality of flow passages have a first configuration, wherein at least some other of the plurality of flow passages have a second configuration different than the first configuration, and wherein the wall thickness adjacent the first configuration is different than the wall thickness adjacent the second configuration.
15. A combo-cooler, comprising:
at least two end tanks; and
a plurality of heat exchangers established between the at least two end tanks, at least one of the plurality of heat exchangers having a tube, including:
a tube body with two opposed sides and a wall having a varying thickness between the two opposed sides; and
a plurality of flow passages defined in the tube body.
16. The combo-cooler as defined in claim 15 wherein each of the plurality of heat exchangers has a tube width ranging from about 8 mm to about 70 mm.
17. The combo-cooler as defined in claim 15 wherein the wall thickness is greatest at or near a center of the tube body, and wherein the wall thickness decreases extending from the center to each of the two opposed sides.
18. The combo-cooler as defined in claim 17 wherein the wall thickness is symmetric from the center to each of the two opposed sides.
19. The combo-cooler as defined in claim 15 , further comprising:
a web formed of the tube body that fluidly separates each of the plurality of flow passages; and
a plurality of micro-fins established on the wall, the web or combinations thereof, such that the plurality of micro-fins extends into at least one of the plurality of flow passages.
20. The combo-cooler as defined in claim 15 wherein the wall has at least two portions, wherein a first of the at least two portions has a first uniform thickness, and wherein a second of the at least two portions has a second uniform thickness that is different from the first uniform thickness.
21. The combo-cooler as defined in claim 15 wherein at least some of the plurality of flow passages have a first configuration, wherein at least some other of the plurality of flow passages have a second configuration different than the first configuration, and wherein the wall thickness adjacent the first configuration is different than the wall thickness adjacent the second configuration.
22. A method for increasing thermal stress resistance of a heat exchanger tube, the method comprising:
varying a thickness of a wall between two opposed sides of a tube body; and
forming a plurality of flow passages in the tube body.
23. The method as defined in claim 22 wherein varying the wall thickness includes increasing the thickness along a width of the tube body extending from each of the two opposed sides toward a predetermined distance from each of the two opposed sides.
24. The method as defined in claim 22 wherein varying the wall thickness includes symmetrically decreasing the thickness from a center of the tube body toward each of the two opposed sides.
25. The method as defined in claim 22 , further comprising:
forming a web of the tube body that fluidly separates each of the plurality of flow passages; and
forming a plurality of micro-fins on the wall, the web or combinations thereof, such that the plurality of micro-fins extends into at least one of the plurality of flow passages.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/963,131 US20090159253A1 (en) | 2007-12-21 | 2007-12-21 | Heat exchanger tubes and combo-coolers including the same |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/963,131 US20090159253A1 (en) | 2007-12-21 | 2007-12-21 | Heat exchanger tubes and combo-coolers including the same |
Publications (1)
Publication Number | Publication Date |
---|---|
US20090159253A1 true US20090159253A1 (en) | 2009-06-25 |
Family
ID=40787210
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/963,131 Abandoned US20090159253A1 (en) | 2007-12-21 | 2007-12-21 | Heat exchanger tubes and combo-coolers including the same |
Country Status (1)
Country | Link |
---|---|
US (1) | US20090159253A1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150090436A1 (en) * | 2013-09-27 | 2015-04-02 | Hamilton Sundstrand Corporation | Fluid based thermal conductivity control |
US20150153116A1 (en) * | 2012-07-27 | 2015-06-04 | Kyocera Corporation | Flow path member, and heat exchanger and semiconductor manufacturing device using same |
US20170038148A1 (en) * | 2013-12-21 | 2017-02-09 | Kyocera Corporation | Heat exchange member and heat exchanger |
EP3134695A4 (en) * | 2014-04-22 | 2017-12-13 | TitanX Engine Cooling Holding AB | Heat exchanger comprising a core of tubes |
JP2018044707A (en) * | 2016-09-14 | 2018-03-22 | 株式会社ケーヒン・サーマル・テクノロジー | Heat exchanger |
WO2023036256A1 (en) * | 2021-09-08 | 2023-03-16 | 杭州三花微通道换热器有限公司 | Heat exchange tube and heat exchanger having heat exchange tube |
Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4570700A (en) * | 1983-01-10 | 1986-02-18 | Nippondenso Co., Ltd. | Flat, multi-luminal tube for cross-flow-type indirect heat exchanger, having greater outer wall thickness towards side externally subject to corrosive inlet gas such as wet, salty air |
US5476141A (en) * | 1993-04-19 | 1995-12-19 | Sanden Corporation | Flat-type refrigerant tube having an improved pressure-resistant strength |
US6192978B1 (en) * | 1999-10-27 | 2001-02-27 | Brazeway, Inc. | Micro-multiport (MMP) tubing with improved metallurgical strength and method for making said tubing |
US6216776B1 (en) * | 1998-02-16 | 2001-04-17 | Denso Corporation | Heat exchanger |
US6289981B1 (en) * | 1997-05-30 | 2001-09-18 | Showa Denko K.K. | Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes |
US6546998B2 (en) * | 2000-12-01 | 2003-04-15 | Lg Electronics Inc. | Tube structure of micro-multi channel heat exchanger |
US20030141048A1 (en) * | 2002-01-31 | 2003-07-31 | Sangok Lee | Heat exchanger tube and heat exchanger using the same |
US6793012B2 (en) * | 2002-05-07 | 2004-09-21 | Valeo, Inc | Heat exchanger |
US6973965B2 (en) * | 2002-12-11 | 2005-12-13 | Modine Manufacturing Company | Heat-exchanger assembly with wedge-shaped tubes with balanced coolant flow |
US20060016583A1 (en) * | 2000-11-02 | 2006-01-26 | Behr Gmbh & Co. | Condenser and tube therefor |
US20060151160A1 (en) * | 2002-10-02 | 2006-07-13 | Showa Denko K.K. | Heat exchanging tube and heat exchanger |
US20080185130A1 (en) * | 2007-02-07 | 2008-08-07 | Behr America | Heat exchanger with extruded cooling tubes |
-
2007
- 2007-12-21 US US11/963,131 patent/US20090159253A1/en not_active Abandoned
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4570700A (en) * | 1983-01-10 | 1986-02-18 | Nippondenso Co., Ltd. | Flat, multi-luminal tube for cross-flow-type indirect heat exchanger, having greater outer wall thickness towards side externally subject to corrosive inlet gas such as wet, salty air |
US5476141A (en) * | 1993-04-19 | 1995-12-19 | Sanden Corporation | Flat-type refrigerant tube having an improved pressure-resistant strength |
US6289981B1 (en) * | 1997-05-30 | 2001-09-18 | Showa Denko K.K. | Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes |
US6216776B1 (en) * | 1998-02-16 | 2001-04-17 | Denso Corporation | Heat exchanger |
US6192978B1 (en) * | 1999-10-27 | 2001-02-27 | Brazeway, Inc. | Micro-multiport (MMP) tubing with improved metallurgical strength and method for making said tubing |
US20060016583A1 (en) * | 2000-11-02 | 2006-01-26 | Behr Gmbh & Co. | Condenser and tube therefor |
US6546998B2 (en) * | 2000-12-01 | 2003-04-15 | Lg Electronics Inc. | Tube structure of micro-multi channel heat exchanger |
US20030141048A1 (en) * | 2002-01-31 | 2003-07-31 | Sangok Lee | Heat exchanger tube and heat exchanger using the same |
US6793012B2 (en) * | 2002-05-07 | 2004-09-21 | Valeo, Inc | Heat exchanger |
US20060151160A1 (en) * | 2002-10-02 | 2006-07-13 | Showa Denko K.K. | Heat exchanging tube and heat exchanger |
US6973965B2 (en) * | 2002-12-11 | 2005-12-13 | Modine Manufacturing Company | Heat-exchanger assembly with wedge-shaped tubes with balanced coolant flow |
US20080185130A1 (en) * | 2007-02-07 | 2008-08-07 | Behr America | Heat exchanger with extruded cooling tubes |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150153116A1 (en) * | 2012-07-27 | 2015-06-04 | Kyocera Corporation | Flow path member, and heat exchanger and semiconductor manufacturing device using same |
US20150090436A1 (en) * | 2013-09-27 | 2015-04-02 | Hamilton Sundstrand Corporation | Fluid based thermal conductivity control |
US20170038148A1 (en) * | 2013-12-21 | 2017-02-09 | Kyocera Corporation | Heat exchange member and heat exchanger |
EP3091323A4 (en) * | 2013-12-21 | 2017-11-15 | Kyocera Corporation | Heat exchanger member and heat exchanger |
US10697707B2 (en) * | 2013-12-21 | 2020-06-30 | Kyocera Corporation | Heat exchange member and heat exchanger |
EP3134695A4 (en) * | 2014-04-22 | 2017-12-13 | TitanX Engine Cooling Holding AB | Heat exchanger comprising a core of tubes |
JP2018044707A (en) * | 2016-09-14 | 2018-03-22 | 株式会社ケーヒン・サーマル・テクノロジー | Heat exchanger |
WO2023036256A1 (en) * | 2021-09-08 | 2023-03-16 | 杭州三花微通道换热器有限公司 | Heat exchange tube and heat exchanger having heat exchange tube |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US11815318B2 (en) | Flattened tube finned heat exchanger and fabrication method | |
EP2810010B1 (en) | Multiple tube bank heat exchanger assembly and fabrication method | |
US20090159253A1 (en) | Heat exchanger tubes and combo-coolers including the same | |
US20130240186A1 (en) | Multiple Tube Bank Flattened Tube Finned Heat Exchanger | |
CN108139183B (en) | heat exchanger | |
US10184732B2 (en) | Air to air heat exchanger | |
US20090065183A1 (en) | Flat heat transfer tube | |
US20090133860A1 (en) | Heat exchanger | |
US20050061488A1 (en) | Automotive heat exchanger | |
US20170211892A1 (en) | Tube for heat exchanger | |
US20120031586A1 (en) | Condenser | |
JPH06185885A (en) | Flat multi-holed condensing and heat transfer pipe | |
US20170050489A1 (en) | Condenser | |
KR20180077188A (en) | heat transmitter | |
US20100147501A1 (en) | Curled manifold for evaporator | |
WO2020223150A1 (en) | Charge air cooler | |
US20150377561A1 (en) | Multiple Bank Flattened Tube Heat Exchanger | |
US7918266B2 (en) | Heat exchanger | |
JP2927051B2 (en) | Heat exchanger | |
JP2017048988A (en) | Heat exchanger | |
JP5079597B2 (en) | Heat exchanger | |
JP3939090B2 (en) | Multi-tube heat exchanger | |
CN210861814U (en) | Heat exchanger and air conditioner with same | |
KR100666927B1 (en) | Heat exchanger of header type | |
JP2016080236A (en) | Heat exchanger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: VALEO INC.,MICHIGAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HU, ZAIQIAN;REEL/FRAME:020637/0245 Effective date: 20080123 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |