US20150211812A1 - Heat exchanger inlet tank with inmolded inlet radius feature - Google Patents
Heat exchanger inlet tank with inmolded inlet radius feature Download PDFInfo
- Publication number
- US20150211812A1 US20150211812A1 US14/165,779 US201414165779A US2015211812A1 US 20150211812 A1 US20150211812 A1 US 20150211812A1 US 201414165779 A US201414165779 A US 201414165779A US 2015211812 A1 US2015211812 A1 US 2015211812A1
- Authority
- US
- United States
- Prior art keywords
- housing
- protuberance
- heat exchanger
- inlet
- inlet tank
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
-
- 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
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into 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
- F28D1/053—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
- F28D1/05308—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
-
- 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
-
- 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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
-
- 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
- F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
- F28F9/0224—Header boxes formed by sealing end plates into covers
Definitions
- the present invention relates to an inlet tank for use with a heat exchanger in a vehicle, and more particularly to an inlet tank radius feature for use with a heat exchanger in a vehicle.
- heat exchangers such as a radiator are configured to change a temperature of various working fluids such as an engine coolant, an engine lubricating oil, an air conditioning refrigerant, and an automatic transmission fluid, for example.
- the heat exchanger typically includes spaced apart fluid conduits or tubes connected between an inlet tank and an outlet tank, and a final disposed between adjacent conduits.
- the working fluid enters the inlet tank through an inlet port, then flows through the fluid conduits or tubes, and exits the outlet tank through an outlet port. Air is directed across the fins. As the air flows across the fins, heat from the working fluid flowing through the tubes is conducted through walls of the tubes, into the fins, and into the air.
- the inlet tank is therefore configured as a fluid manifold to distribute the working fluid from the inlet port to the tubes.
- the inlet tank typically includes a housing and an inlet connector or pipe that defines the inlet port.
- the inlet connector is typically formed in a side of the housing and extends outwardly therefrom.
- the inlet connector may be configured for coupling to a pipeline or hose of a vehicle in order to feed the circulating working fluid into the inlet tank.
- a sharp edge is formed at an inlet interface on an inner surface of the housing and an inner surface of the inlet connector.
- the sharp edge disrupts a bulk velocity of the working fluid flowing through the inlet tank which results in an increase in a pressure drop of the working fluid as the working fluid enters the inlet tank.
- the increase in the pressure drop reduces a thermal efficiency of the radiator. Therefore, it is desirable to form a radiused inlet edge on the inlet connector at the inlet interface instead of a sharp edge to minimize the pressure drop of the working fluid as the working fluid enters the inlet tank.
- inlet tanks for heat exchangers are typically formed by a molding process, wherein the inlet tank and the inlet connector are formed integrally. Due to a direction of draw of molding tools, forming the inlet connector requires a special molding device such as a core or cavity projection that will retract during the molding process. Forming a feature on the inlet connector to form a radiused inlet edge complicates a design of the molding tool and a design of the special molding device and increases the cost of the molding process.
- a heat exchanger inlet tank includes a housing having an inner surface and an outer surface and an inlet connector having an inner surface substantially continuous with the inner surface of the housing.
- the inner surface of the inlet connector and the inner surface of the housing converge to form an inlet interface.
- the heat exchanger inlet tank further includes a protuberance disposed on the inner surface of the housing configured to militate against a pressure drop of a fluid flowing through the inlet tank.
- a heat exchanger inlet tank includes a housing having an inner surface and an outer surface and an inlet connector integrally formed with and extending outwardly from the outer surface of the housing.
- the inlet connector having an inner surface substantially continuous with the inner surface of the housing.
- the heat exchanger inlet tank further includes an inlet interface formed at a convergence of the inner surface of the housing and the inner surface of the inlet connector and a protuberance disposed on the inner surface of the housing extending from at least a portion of the inlet interface along the inner surface of the housing.
- a heat exchanger includes an inlet tank including a housing having an inner surface and an outer surface and an inlet connector having an inner surface substantially continuous with the inner surface of the housing. The inner surface of the inlet connector and the inner surface of the housing converging to form an inlet interface.
- the heat exchanger further includes a protuberance having a substantially arcuate cross-section disposed on the inner surface of the housing extending from at least a portion of the inlet interface along the inner surface of the housing to a transitional portion of the inner surface of the housing.
- a concave indentation corresponding to the protuberance is formed on the outer surface of the housing.
- a plurality of tubes extend from and are in fluid communication with the inlet tank.
- FIG. 1 is a fragmentary top perspective view of a heat exchanger according to an embodiment of the invention
- FIG. 2 is a fragmentary bottom plan view of an inlet tank of the heat exchanger illustrated in FIG. 1 ;
- FIG. 3 is a fragmentary bottom perspective view of the inlet tank of FIGS. 1 and 2 ;
- FIG. 4 is a broken rear elevational view of the inlet tank of the heat exchanger illustrated in FIG. 1 ;
- FIG. 5 is a cross-sectional view taken along the line 5 - 5 of FIG. 4 ;
- FIG. 6 is a fragmentary cross-sectional view taken along the line 6 - 6 of FIG. 4 ;
- FIG. 7 is a cross-sectional view taken along the line 5 - 5 of FIG. 4 according to another embodiment of the invention.
- FIG. 8 is a fragmentary cross-sectional view taken along the line 6 - 6 of FIG. 4 according to another embodiment of the invention.
- FIG. 1 illustrates a heat exchanger 10 according to an embodiment of the invention.
- the heat exchanger 10 can be used, for example, as a radiator for cooling a liquid coolant for an engine of a vehicle.
- the heat exchanger 10 includes a heat exchange core 12 and a housing 20 .
- the heat exchange core 12 includes a plurality of substantially parallel tubes 14 and a plurality of substantially parallel fins 16 interposed between the tubes 12 .
- the heat exchanger 10 is a parallel flow type heat exchanger commonly referred to as a radiator.
- other types of heat exchangers can be used such as a serpentine-flow type heat exchanger and a U-flow type heat exchanger.
- the embodiment shown includes the heat exchange core 12 with the tubes 14 and the fins 16 , it is understood the invention can be used in conjunction with various types of heat exchange cores.
- the tubes 14 are configured to contain and convey a fluid to facilitate heat transfer.
- the fluid can be any fluid configured to facilitate heat transfer such as engine coolant, an engine lubricating oil, an air conditioning refrigerant, and an automatic transmission fluid, for example.
- the tubes 14 extend laterally from and are in fluid communication with the housing 20 . Further, the tubes 14 extend substantially perpendicular relative to the housing 20 .
- the tubes 14 can extend between the housing 20 and an outlet tank (not shown) adapted to provide an exit for the fluid flowing through the heat exchanger 10 .
- the fins 16 are in thermal communication with the tubes 14 and are adapted to allow a flow of air to pass therebetween, and further allow the flow of air to pass between the tubes 14 to facilitate transfer of heat from the air to the fins 16 to the tubes 14 and to the fluid or from the fluid to the tubes 14 to the fins 16 and to the air.
- the fins 16 may have a corrugated shape.
- the housing 20 is elongate and adapted to convey a flow of the fluid from a source of fluid (not shown) to the tubes 14 .
- the housing 20 includes a chamber 30 having a tube perimeter 22 defining an opening 28 .
- the housing 20 further includes a substantially arcuate wall 24 extending between opposing end walls 26 , a substantially smooth inner surface 34 , and an outer surface 35 .
- the arcuate wall 24 and the end walls 26 extend from the tube perimeter 22 to form the chamber 30 to receive the fluid.
- the chamber 30 can be enclosed by a plate not shown) disposed in the opening 28 with a plurality of tube openings (not shown) for receiving the tubes 14 .
- the plate is bounded by the tube perimeter 22 and can be integrally formed with the housing 20 or the plate can be separately formed from the housing 20 and coupled thereto.
- the housing 20 has a substantially semi-cylindrical shape.
- the housing 20 can have a rectangular shape having five walls or any other shape as desired such as around, ovular, ellipsoidal, and triangular, for example.
- the housing 20 further includes an inlet connector 40 disposed at a first end 32 thereof and adapted to provide fluid communication between the source of fluid and the housing 20 .
- the inlet connector 40 is integrally formed with the housing 20 and extends outwardly from the outer surface 35 of the housing 20 .
- the inlet connector 40 defines an inlet port 42 to the chamber 30 .
- the inlet connector 40 is substantially perpendicular in respect of a longitudinal direction of the housing 20 .
- the inlet connector 40 can also be formed at an angle in respect of the housing 20 .
- the inlet connector 40 has a generally cylindrical shape and has an inner diameter d. In the embodiment shown, the inlet connector 40 has a truncated cylindrical shape due to the semi-cylindrical shape of the housing 20 .
- the inlet connector 40 can have any shape as desired. Additionally, the inlet connector 40 can extend from any position on the housing 20 such as a center, one of the opposing end walls 26 , or a second end 33 , for example.
- a substantially smooth inner surface 44 of the inlet connector 40 is substantially continuous with the substantially smooth inner surface 34 of the housing 20 .
- the inner surface 44 of the inlet connector 40 and the inner surface 34 of the housing 20 converge to form an inlet interface 50 .
- the inlet interface 50 includes a first edge portion 52 and a second edge portion 54 .
- the first edge portion 52 corresponds to a portion of the inlet interface 50 that extends along a first arc of curvature a 1 thereof.
- the second edge portion 54 corresponds to a portion of the inlet interface 50 that extends along a second arc of curvature a 2 thereof.
- the first edge portion 52 corresponds to a portion of the inlet interface 50 where an edge radius can be formed, where an edge radius is an arcuate or rounded edge. It is understood that the first edge portion 52 can also extend along the entire inlet interface 50 .
- the housing 20 further includes a protuberance 60 integrally formed with and extending outwardly from the inner surface 34 of the housing 20 .
- the protuberance 60 is generally convex with respect to the inner surface 34 of the housing 20 .
- the protuberance 60 is substantially continuous with the inlet interface 50 and extends longitudinally along the inner surface 34 of the housing 20 from the first edge portion 52 of the inlet interface 50 towards the second end 33 of the housing 20 to a transitional portion 38 of the inner surface 32 of the housing 20 .
- the transitional portion 38 and the first edge portion 52 of the inlet interface 30 form a perimeter of the protuberance 60 .
- a width w p of the protuberance 60 can vary along a length l p thereof and the length l p of the protuberance 60 can vary along a width w p thereof.
- the protuberance 60 has a generally parabolic or slightly crescent shaped perimeter.
- the protuberance 60 can have a perimeter having any shape as desired such as fan shaped, rectangular, kidney shaped, ovular, or any other shape to minimize a pressure drop of the fluid flowing through the housing 20 .
- the protuberance 60 has a cross-section that is generally arcuate or camber-shaped to facilitate a smooth flow of the fluid through the housing 20 .
- the protuberance 60 can have other cross-sectional shapes as desired such as a serpentine shaped, saddle shaped, semi-circular shaped, wedge shaped, or any other shape as desired to minimize a pressure drop of the fluid flowing through the housing 20 .
- a height h p of the protuberance 60 with respect of the inner surface 34 of the housing 20 varies along the width thereof w p .
- the protuberance 60 has a first tapered side 66 tapering towards the tube perimeter 22 to the transitional portion 38 .
- the protuberance 60 also has a second tapered side 68 tapering towards a base 36 of the arcuate wall 24 to the transitional portion 38 of the inner surface 34 of the housing 20 such that a substantially smooth surface is formed at the transition portion 38 .
- a width w T1 of the first tapered side 66 can be substantially equal to a width w T2 of the second tapered side 68 .
- the width w T1 of the first tapered side 66 can be smaller or larger than the width w T2 of second tapered end 68 to facilitate minimizing a pressure drop of the fluid flowing through the housing 20 , as desired.
- the width w T1 of the first tapered side 66 can be less than the width w T2 of the second tapered side 68 .
- the first tapered side 66 can have a taper that is steeper than the second tapered side 68 or the second tapered side 68 can have a steeper taper than the first tapered side 66 .
- the protuberance 60 slightly curves along the width w p thereof with the inner surface 34 of the housing 20 to provide an substantially smooth transition at the transitional portion 38 and to conform to the semi-cylindrical cross-sectional shape of the housing 20 .
- the protruberance 60 can be adapted to conform to any shape of the housing 20 as desired such as a rectangular shape having five walls or any other shape as desired, such as obround, ovular, ellipsoidal, and triangular, for example.
- the protuberance 60 has a cross-section that is arcuate or camber-shaped to facilitate a smooth flow of fluid through the housing 20 .
- the protuberance can have other cross-sectional shapes as desired such as a serpentine shaped, saddle shaped, semi-circular, wedge shaped, or any other shape as desired to minimize a pressure drop of the fluid across the protuberance 60 and through the housing 20 .
- the height h p of the protuberance 60 with respect of the inner surface 34 of the housing 20 varies along a length l p thereof As shown in FIG.
- the protuberance 60 has a first tapered end 62 tapering towards the inlet interface 50 forming the radiused edge at the inlet interface 50 .
- the protuberance 60 can also have a second tapered end 64 tapering towards the second end 33 of the housing 20 to the transitional portion 38 of the inner surface 34 of the housing 20 such that a substantially smooth surface is formed at the transition portion 38 .
- a length l T1 of the first tapered end 62 is substantially equal to a length l T2 of the second tapered end 64 .
- the length l T2 of the first tapered end 62 can be smaller or larger than the length l T2 of second tapered end 64 to facilitate minimizing a pressure drop of the fluid across the protuberance 60 and through the housing 20 , as desired.
- the length l T1 of the first tapered end 62 can be less than the length l T2 of the second tapered end 64 such that the first tapered end 62 has as steeper taper than the taper of the second tapered end 64 .
- the first tapered end 62 can have a taper that is steeper than the taper of the second tapered end 64 and the second tapered end 64 can have a taper that is steeper than the taper of the first tapered end 62 .
- the housing 20 has a wall thickness t c .
- the protuberance 60 has a wall thickness t p larger than the wall thickness t 1p of the housing 20 .
- the wall thickness l p of the protuberance can vary as the height h p varies along the length l p and the width w p thereof.
- FIG. 7 and FIG. 8 illustrate another embodiment. Structure similar to FIG. 5 and FIG. 6 includes the same reference numeral and a prime 0 symbol for clarity.
- the wall thickness t p′ of the protuberance 60 ′ can be substantially uniform with and substantially equal to the wall thickness of the housing 20 ′ to facilitate an improved molding process.
- a concave indentation 170 is formed on the outer surface 35 ′ of the housing 20 ′.
- the concave indentation 170 corresponds to the protuberance 60 ′ and is adapted to conform with the shape of the protuberance 60 ′ on the inner surface 34 ′ of the housing 20 ′ to maintain a uniform thickness between the thickness t c′ of the housing 20 ′ and the thickness t p′ of the protuberance 60 ′.
- the protuberance 60 can have any shape, length l p , width w p , thickness t p or height h p as desired to minimize the pressure drop of the fluid flowing through the housing 20 .
- the length l p and the width w p of the protuberance 60 can be 1 to 2 times the inner diameter d of the inlet connector 40 .
- the height h p of the protuberance 60 in respect of the inner surface 34 of the housing 20 can be 0.08-0.2 times the inner diameter d of the inlet connector 40 .
- the protuberance 60 shown in FIG. 3 only circumscribes a portion of the inlet port 42 at the first edge portion 52 , it is understood the protuberance 60 can circumscribe any portion of inlet port 42 such as circumscribing the entire inlet port 42 .
- the housing 20 can be composed of plastic and formed from a molding process such as injection molding, for example.
- the protuberance 60 can be formed by a feature on a mold in an injection molding process such that the protuberance 60 is integrally molded with the housing 20 .
- the housing 20 and the protuberance 60 can be adapted to allow for adequate molding die draw.
- the protuberance 60 is tapered to facilitate removal from the mold.
- the housing 20 and the protuberance 60 can be formed by other processes such as metal stamping, for example.
- the housing 20 and the protuberance 60 can be formed employing other suitable methods now known or later developed. Additionally, the protuberance 60 can be separately formed and coupled with the housing 20 , as desired.
- the fluid is caused to flow from the source of fluid through the housing 20 to be distributed to the tubes 14 .
- the fluid can be any conventional fluid such as a coolant fluid, an automatic transmission fluid, a power steering fluid, or an engine oil, for example.
- the fluid enters the housing 20 by flowing through the inlet connector 40 and then flowing into the chamber 30 at a bulk velocity.
- the fluid flows over the protuberance 60 which forms the radiused edge at the inlet interface 50 .
- the protuberance 60 is adapted to minimize a decrease in bulk velocity of the fluid as the fluid transitions from the inlet connector 40 to the chamber 30 .
- the protuberance 60 on the housing 20 can be adapted to minimize the pressure drop from the inlet connector 40 to the chamber 30 by about 10 % to 15% of a pressure drop of the housing 20 without the protuberance 60 .
- lower or higher percentages can be realized depending on the type of housing 20 and the height h p , length l p , width w p , and thickness l p of the protuberance 60 .
- the protuberance 60 disposed on the housing 20 facilitates an ease of manufacturing and decreases a cost of manufacturing.
- a special retraction tool is not required for the forming of the connection inlet 40 in the molding process to militate against an inadequate molding die draw.
- embodiments shown in the illustrated figures show a protuberance 60 disposed within the housing 20 to form a radiused edge at the inlet interface 50 , it is understood the protuberance 60 can be included with a housing 20 having a feature formed on or included with the inlet connector 40 to also facilitate forming a radiused edge to militate against a pressure drop in the housing 20 .
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A heat exchanger inlet tank including a housing having an inner surface and an outer surface and an inlet connector having an inner surface substantially continuous with the inner surface of the housing. The inner surface of the inlet connector and the inner surface of the housing converging to form an inlet interface. The heat exchanger further includes a protuberance disposed on the inner surface of the housing configured to militate against a pressure drop of a fluid flowing through the inlet tank.
Description
- The present invention relates to an inlet tank for use with a heat exchanger in a vehicle, and more particularly to an inlet tank radius feature for use with a heat exchanger in a vehicle.
- As commonly known, heat exchangers such as a radiator are configured to change a temperature of various working fluids such as an engine coolant, an engine lubricating oil, an air conditioning refrigerant, and an automatic transmission fluid, for example. The heat exchanger typically includes spaced apart fluid conduits or tubes connected between an inlet tank and an outlet tank, and a final disposed between adjacent conduits. The working fluid enters the inlet tank through an inlet port, then flows through the fluid conduits or tubes, and exits the outlet tank through an outlet port. Air is directed across the fins. As the air flows across the fins, heat from the working fluid flowing through the tubes is conducted through walls of the tubes, into the fins, and into the air. The inlet tank is therefore configured as a fluid manifold to distribute the working fluid from the inlet port to the tubes.
- The inlet tank typically includes a housing and an inlet connector or pipe that defines the inlet port. The inlet connector is typically formed in a side of the housing and extends outwardly therefrom. The inlet connector may be configured for coupling to a pipeline or hose of a vehicle in order to feed the circulating working fluid into the inlet tank. A sharp edge is formed at an inlet interface on an inner surface of the housing and an inner surface of the inlet connector. Undesirably, the sharp edge disrupts a bulk velocity of the working fluid flowing through the inlet tank which results in an increase in a pressure drop of the working fluid as the working fluid enters the inlet tank. The increase in the pressure drop reduces a thermal efficiency of the radiator. Therefore, it is desirable to form a radiused inlet edge on the inlet connector at the inlet interface instead of a sharp edge to minimize the pressure drop of the working fluid as the working fluid enters the inlet tank.
- However, inlet tanks for heat exchangers are typically formed by a molding process, wherein the inlet tank and the inlet connector are formed integrally. Due to a direction of draw of molding tools, forming the inlet connector requires a special molding device such as a core or cavity projection that will retract during the molding process. Forming a feature on the inlet connector to form a radiused inlet edge complicates a design of the molding tool and a design of the special molding device and increases the cost of the molding process.
- Therefore, it would be desirable to produce an inlet tank of a heat exchanger having a feature to form a radiused inlet edge, wherein a thermal efficiency of the heat exchanger is maximized and complexity of manufacturing and costs are minimized. It would be advantageous if an inlet tank of a heat exchanger could be improved.
- Concordant and congruous with the present invention, an improvement of an inlet tank of a heat exchanger has been discovered.
- According to an embodiment a heat exchanger inlet tank is disclosed. The heat exchanger inlet tank includes a housing having an inner surface and an outer surface and an inlet connector having an inner surface substantially continuous with the inner surface of the housing. The inner surface of the inlet connector and the inner surface of the housing converge to form an inlet interface. The heat exchanger inlet tank further includes a protuberance disposed on the inner surface of the housing configured to militate against a pressure drop of a fluid flowing through the inlet tank.
- According to another embodiment a heat exchanger inlet tank includes a housing having an inner surface and an outer surface and an inlet connector integrally formed with and extending outwardly from the outer surface of the housing. The inlet connector having an inner surface substantially continuous with the inner surface of the housing. The heat exchanger inlet tank further includes an inlet interface formed at a convergence of the inner surface of the housing and the inner surface of the inlet connector and a protuberance disposed on the inner surface of the housing extending from at least a portion of the inlet interface along the inner surface of the housing.
- According to a further embodiment a heat exchanger is disclosed. The heat exchanger includes an inlet tank including a housing having an inner surface and an outer surface and an inlet connector having an inner surface substantially continuous with the inner surface of the housing. The inner surface of the inlet connector and the inner surface of the housing converging to form an inlet interface. The heat exchanger further includes a protuberance having a substantially arcuate cross-section disposed on the inner surface of the housing extending from at least a portion of the inlet interface along the inner surface of the housing to a transitional portion of the inner surface of the housing. A concave indentation corresponding to the protuberance is formed on the outer surface of the housing. A plurality of tubes extend from and are in fluid communication with the inlet tank.
- The above, as well as other advantages of the present invention, will become readily apparent to those skilled in the art from the following detailed description of a preferred embodiment when considered in the light of the accompanying drawings in which:
-
FIG. 1 is a fragmentary top perspective view of a heat exchanger according to an embodiment of the invention; -
FIG. 2 is a fragmentary bottom plan view of an inlet tank of the heat exchanger illustrated inFIG. 1 ; -
FIG. 3 is a fragmentary bottom perspective view of the inlet tank ofFIGS. 1 and 2 ; -
FIG. 4 is a broken rear elevational view of the inlet tank of the heat exchanger illustrated inFIG. 1 ; -
FIG. 5 is a cross-sectional view taken along the line 5-5 ofFIG. 4 ; -
FIG. 6 is a fragmentary cross-sectional view taken along the line 6-6 ofFIG. 4 ; -
FIG. 7 is a cross-sectional view taken along the line 5-5 ofFIG. 4 according to another embodiment of the invention; and -
FIG. 8 is a fragmentary cross-sectional view taken along the line 6-6 ofFIG. 4 according to another embodiment of the invention. - The following detailed description and appended drawings describe and illustrate various exemplary embodiments of the invention. The description and drawings serve to enable one skilled in the art to make and use the invention, and are not intended to limit the scope of the invention in any manner.
-
FIG. 1 illustrates aheat exchanger 10 according to an embodiment of the invention. Theheat exchanger 10 can be used, for example, as a radiator for cooling a liquid coolant for an engine of a vehicle. Theheat exchanger 10 includes aheat exchange core 12 and ahousing 20. Theheat exchange core 12 includes a plurality of substantiallyparallel tubes 14 and a plurality of substantiallyparallel fins 16 interposed between thetubes 12. In the embodiment shown, theheat exchanger 10 is a parallel flow type heat exchanger commonly referred to as a radiator. However, it should be understood that other types of heat exchangers can be used such as a serpentine-flow type heat exchanger and a U-flow type heat exchanger. Additionally, while the embodiment shown includes theheat exchange core 12 with thetubes 14 and thefins 16, it is understood the invention can be used in conjunction with various types of heat exchange cores. - The
tubes 14 are configured to contain and convey a fluid to facilitate heat transfer. The fluid can be any fluid configured to facilitate heat transfer such as engine coolant, an engine lubricating oil, an air conditioning refrigerant, and an automatic transmission fluid, for example. Thetubes 14 extend laterally from and are in fluid communication with thehousing 20. Further, thetubes 14 extend substantially perpendicular relative to thehousing 20. Thetubes 14 can extend between thehousing 20 and an outlet tank (not shown) adapted to provide an exit for the fluid flowing through theheat exchanger 10. Thefins 16 are in thermal communication with thetubes 14 and are adapted to allow a flow of air to pass therebetween, and further allow the flow of air to pass between thetubes 14 to facilitate transfer of heat from the air to thefins 16 to thetubes 14 and to the fluid or from the fluid to thetubes 14 to thefins 16 and to the air. Thefins 16 may have a corrugated shape. - As shown in
FIGS. 1-3 , thehousing 20 is elongate and adapted to convey a flow of the fluid from a source of fluid (not shown) to thetubes 14. Thehousing 20 includes achamber 30 having atube perimeter 22 defining anopening 28. Thehousing 20 further includes a substantiallyarcuate wall 24 extending between opposingend walls 26, a substantially smoothinner surface 34, and anouter surface 35. Thearcuate wall 24 and theend walls 26 extend from thetube perimeter 22 to form thechamber 30 to receive the fluid. Thechamber 30 can be enclosed by a plate not shown) disposed in theopening 28 with a plurality of tube openings (not shown) for receiving thetubes 14. The plate is bounded by thetube perimeter 22 and can be integrally formed with thehousing 20 or the plate can be separately formed from thehousing 20 and coupled thereto. In the embodiment shown, thehousing 20 has a substantially semi-cylindrical shape. However, thehousing 20 can have a rectangular shape having five walls or any other shape as desired such as around, ovular, ellipsoidal, and triangular, for example. - The
housing 20 further includes aninlet connector 40 disposed at afirst end 32 thereof and adapted to provide fluid communication between the source of fluid and thehousing 20. As shown, theinlet connector 40 is integrally formed with thehousing 20 and extends outwardly from theouter surface 35 of thehousing 20. Theinlet connector 40 defines aninlet port 42 to thechamber 30. Theinlet connector 40 is substantially perpendicular in respect of a longitudinal direction of thehousing 20. However, theinlet connector 40 can also be formed at an angle in respect of thehousing 20. Theinlet connector 40 has a generally cylindrical shape and has an inner diameter d. In the embodiment shown, theinlet connector 40 has a truncated cylindrical shape due to the semi-cylindrical shape of thehousing 20. However, theinlet connector 40 can have any shape as desired. Additionally, theinlet connector 40 can extend from any position on thehousing 20 such as a center, one of the opposingend walls 26, or asecond end 33, for example. - A substantially smooth
inner surface 44 of theinlet connector 40 is substantially continuous with the substantially smoothinner surface 34 of thehousing 20. Theinner surface 44 of theinlet connector 40 and theinner surface 34 of thehousing 20 converge to form aninlet interface 50. Theinlet interface 50 includes afirst edge portion 52 and asecond edge portion 54. Thefirst edge portion 52 corresponds to a portion of theinlet interface 50 that extends along a first arc of curvature a1 thereof. Thesecond edge portion 54 corresponds to a portion of theinlet interface 50 that extends along a second arc of curvature a2 thereof. Thefirst edge portion 52 corresponds to a portion of theinlet interface 50 where an edge radius can be formed, where an edge radius is an arcuate or rounded edge. It is understood that thefirst edge portion 52 can also extend along theentire inlet interface 50. - The
housing 20 further includes aprotuberance 60 integrally formed with and extending outwardly from theinner surface 34 of thehousing 20. Theprotuberance 60 is generally convex with respect to theinner surface 34 of thehousing 20. Theprotuberance 60 is substantially continuous with theinlet interface 50 and extends longitudinally along theinner surface 34 of thehousing 20 from thefirst edge portion 52 of theinlet interface 50 towards thesecond end 33 of thehousing 20 to atransitional portion 38 of theinner surface 32 of thehousing 20. Thetransitional portion 38 and thefirst edge portion 52 of theinlet interface 30 form a perimeter of theprotuberance 60. A width wp of theprotuberance 60 can vary along a length lp thereof and the length lp of theprotuberance 60 can vary along a width wp thereof. In the embodiment shown, theprotuberance 60 has a generally parabolic or slightly crescent shaped perimeter. However, theprotuberance 60 can have a perimeter having any shape as desired such as fan shaped, rectangular, kidney shaped, ovular, or any other shape to minimize a pressure drop of the fluid flowing through thehousing 20. - In the embodiment shown in
FIG. 5 , theprotuberance 60 has a cross-section that is generally arcuate or camber-shaped to facilitate a smooth flow of the fluid through thehousing 20. However, it is understood, theprotuberance 60 can have other cross-sectional shapes as desired such as a serpentine shaped, saddle shaped, semi-circular shaped, wedge shaped, or any other shape as desired to minimize a pressure drop of the fluid flowing through thehousing 20. A height hp of theprotuberance 60 with respect of theinner surface 34 of thehousing 20 varies along the width thereof wp. For example, as shown inFIG. 5 , theprotuberance 60 has a firsttapered side 66 tapering towards thetube perimeter 22 to thetransitional portion 38. Theprotuberance 60 also has a secondtapered side 68 tapering towards abase 36 of thearcuate wall 24 to thetransitional portion 38 of theinner surface 34 of thehousing 20 such that a substantially smooth surface is formed at thetransition portion 38. A width wT1 of the firsttapered side 66 can be substantially equal to a width wT2 of the secondtapered side 68. However, the width wT1 of the firsttapered side 66 can be smaller or larger than the width wT2 of secondtapered end 68 to facilitate minimizing a pressure drop of the fluid flowing through thehousing 20, as desired. In a non-limiting example as shown inFIG. 5 , the width wT1 of the firsttapered side 66 can be less than the width wT2 of the secondtapered side 68. Additionally, the firsttapered side 66 can have a taper that is steeper than the secondtapered side 68 or the secondtapered side 68 can have a steeper taper than the firsttapered side 66. Furthermore, as shown inFIG. 5 , theprotuberance 60 slightly curves along the width wp thereof with theinner surface 34 of thehousing 20 to provide an substantially smooth transition at thetransitional portion 38 and to conform to the semi-cylindrical cross-sectional shape of thehousing 20. However, it is understood that theprotruberance 60 can be adapted to conform to any shape of thehousing 20 as desired such as a rectangular shape having five walls or any other shape as desired, such as obround, ovular, ellipsoidal, and triangular, for example. - In the embodiment shown in
FIG. 6 , theprotuberance 60 has a cross-section that is arcuate or camber-shaped to facilitate a smooth flow of fluid through thehousing 20. However, it is understood, the protuberance can have other cross-sectional shapes as desired such as a serpentine shaped, saddle shaped, semi-circular, wedge shaped, or any other shape as desired to minimize a pressure drop of the fluid across theprotuberance 60 and through thehousing 20. The height hp of theprotuberance 60 with respect of theinner surface 34 of thehousing 20 varies along a length lp thereof As shown inFIG. 6 , theprotuberance 60 has a firsttapered end 62 tapering towards theinlet interface 50 forming the radiused edge at theinlet interface 50. Theprotuberance 60 can also have a secondtapered end 64 tapering towards thesecond end 33 of thehousing 20 to thetransitional portion 38 of theinner surface 34 of thehousing 20 such that a substantially smooth surface is formed at thetransition portion 38. A length lT1 of the firsttapered end 62 is substantially equal to a length lT2 of the secondtapered end 64. However, the length lT2 of the firsttapered end 62 can be smaller or larger than the length lT2 of secondtapered end 64 to facilitate minimizing a pressure drop of the fluid across theprotuberance 60 and through thehousing 20, as desired. In a non-limiting example, the length lT1 of the firsttapered end 62 can be less than the length lT2 of the secondtapered end 64 such that the firsttapered end 62 has as steeper taper than the taper of the secondtapered end 64. Additionally, the firsttapered end 62 can have a taper that is steeper than the taper of the secondtapered end 64 and the secondtapered end 64 can have a taper that is steeper than the taper of the firsttapered end 62. - In the embodiment shown in
FIG. 5 andFIG. 6 , thehousing 20 has a wall thickness tc. Theprotuberance 60 has a wall thickness tp larger than the wall thickness t1p of thehousing 20. The wall thickness lp of the protuberance can vary as the height hp varies along the length lp and the width wp thereof. However,FIG. 7 andFIG. 8 illustrate another embodiment. Structure similar toFIG. 5 andFIG. 6 includes the same reference numeral and a prime 0 symbol for clarity. The wall thickness tp′ of theprotuberance 60′ can be substantially uniform with and substantially equal to the wall thickness of thehousing 20′ to facilitate an improved molding process. According to this embodiment, aconcave indentation 170 is formed on theouter surface 35′ of thehousing 20′. Theconcave indentation 170 corresponds to theprotuberance 60′ and is adapted to conform with the shape of theprotuberance 60′ on theinner surface 34′ of thehousing 20′ to maintain a uniform thickness between the thickness tc′ of thehousing 20′ and the thickness tp′ of theprotuberance 60′. - The
protuberance 60 can have any shape, length lp, width wp, thickness tp or height hp as desired to minimize the pressure drop of the fluid flowing through thehousing 20. In a non-limiting example, the length lp and the width wp of theprotuberance 60 can be 1 to 2 times the inner diameter d of theinlet connector 40. In another non-limiting example, the height hp of theprotuberance 60 in respect of theinner surface 34 of thehousing 20 can be 0.08-0.2 times the inner diameter d of theinlet connector 40. Additionally, while theprotuberance 60 shown inFIG. 3 , only circumscribes a portion of theinlet port 42 at thefirst edge portion 52, it is understood theprotuberance 60 can circumscribe any portion ofinlet port 42 such as circumscribing theentire inlet port 42. - The
housing 20 can be composed of plastic and formed from a molding process such as injection molding, for example. Theprotuberance 60 can be formed by a feature on a mold in an injection molding process such that theprotuberance 60 is integrally molded with thehousing 20. Thehousing 20 and theprotuberance 60 can be adapted to allow for adequate molding die draw. For example, theprotuberance 60 is tapered to facilitate removal from the mold. It should be understood that thehousing 20 and theprotuberance 60 can be formed by other processes such as metal stamping, for example. Although thehousing 20 and theprotuberance 60 can be formed employing other suitable methods now known or later developed. Additionally, theprotuberance 60 can be separately formed and coupled with thehousing 20, as desired. - In use, the fluid is caused to flow from the source of fluid through the
housing 20 to be distributed to thetubes 14. The fluid can be any conventional fluid such as a coolant fluid, an automatic transmission fluid, a power steering fluid, or an engine oil, for example. The fluid enters thehousing 20 by flowing through theinlet connector 40 and then flowing into thechamber 30 at a bulk velocity. As the fluid flows from theinlet connector 40 to thechamber 30, the fluid flows over theprotuberance 60 which forms the radiused edge at theinlet interface 50. Theprotuberance 60 is adapted to minimize a decrease in bulk velocity of the fluid as the fluid transitions from theinlet connector 40 to thechamber 30. Minimizing a decrease in the bulk velocity of the fluid militates against a pressure drop of the fluid as the fluid transitions from theinlet connector 40 to thechamber 30, which in turn increases thermal efficiency of theheat exchanger 10. For example, theprotuberance 60 on thehousing 20 can be adapted to minimize the pressure drop from theinlet connector 40 to thechamber 30 by about 10% to 15% of a pressure drop of thehousing 20 without theprotuberance 60. However, lower or higher percentages can be realized depending on the type ofhousing 20 and the height hp, length lp, width wp, and thickness lp of theprotuberance 60. - Further, the
protuberance 60 disposed on thehousing 20 facilitates an ease of manufacturing and decreases a cost of manufacturing. For injection molding, because theprotuberance 60 is disposed on thehousing 20, a special retraction tool is not required for the forming of theconnection inlet 40 in the molding process to militate against an inadequate molding die draw. While, embodiments shown in the illustrated figures, show aprotuberance 60 disposed within thehousing 20 to form a radiused edge at theinlet interface 50, it is understood theprotuberance 60 can be included with ahousing 20 having a feature formed on or included with theinlet connector 40 to also facilitate forming a radiused edge to militate against a pressure drop in thehousing 20. - From the foregoing description, one ordinarily skilled in the art can easily ascertain the essential characteristics of this invention and, without departing from the spirit and scope thereof, can make various changes and modifications to the invention to adapt it to various usages and conditions.
Claims (20)
1. A heat exchanger inlet tank, comprising:
a housing having an inner surface and an outer surface;
an inlet connector having an inner surface substantially continuous with the inner surface of the housing, the inner surface of the inlet connector and the inner surface of the housing converging to form an inlet interface; and
a protuberance disposed on the inner surface of the housing configured to militate against a pressure drop of a fluid flowing through the inlet tank.
2. The heat exchanger inlet tank of claim 1 , wherein the protuberance extends from at least a portion of the inlet interface to a transitional portion of the inner surface of the housing.
3. The heat exchanger inlet tank of claim 2 , wherein the protuberance has a first tapered side, a second tapered side, a first tapered end, and a second tapered end, the first tapered side, the second tapered side, and the second tapered end tapering to the transitional portion, and the first tapered end tapering to the inlet interface.
4. The heat exchanger inlet tank of claim 1 , wherein the protuberance forms a radiused edge at the inlet interface.
5. The heat exchanger inlet tank of claim 1 , wherein the protuberance has a width varying along a length thereof.
6. The heat exchanger inlet tank of claim 1 , wherein the protuberance has a length that varies along a width thereof.
7. The heat exchanger inlet tank of claim 1 , wherein the protuberance has an arcuate cross-section.
8. The heat exchanger inlet tank of claim 1 , wherein a height of the protuberance in respect of the inner surface of the housing varies along a length of the protuberance.
9. The heat exchanger inlet tank of claim 1 , wherein a height of the protuberance in respect of the inner surface of the housing varies along a width of the protuberance.
10. The heat exchanger inlet tank of claim 1 , wherein a wall thickness of the protuberance is substantially equal to a wall thickness of the housing.
11. The heat exchanger inlet tank of claim 1 , wherein a concave indentation corresponding to the protuberance is formed on the outer surface of the housing.
12. The heat exchanger inlet tank of claim 1 , wherein the protuberance is integrally formed by one of injection molding and metal stamping.
13. The heat exchanger inlet tank of claim 1 , wherein the housing has a substantially semi-circular shape
14. A heat exchanger inlet tank, comprising:
a housing having an inner surface and an outer surface;
an inlet connector integrally formed with and extending outwardly from the outer surface of the housing, the inlet connector having an inner surface substantially continuous with the inner surface of the housing;
an inlet interface formed at a convergence of the inner surface of the housing and the inner surface of the inlet connector; and
a protuberance disposed on the inner surface of the housing extending from at least a portion of the inlet interface along the inner surface of the housing.
15. The heat exchanger inlet tank of claim 13 , wherein the protuberance has at least one of a width varying along a length thereof and a length that varies along a width thereof.
16. The heat exchanger inlet tank of claim 13 , wherein the protuberance extends from the at least a portion of the inlet interface to a transitional portion of the inner surface of the housing.
17. The heat exchanger inlet tank of claim 13 , wherein a height of the protuberance in respect of the inner surface of the housing varies along a length of the protuberance.
18. The heat exchanger inlet tank of claim 13 , wherein a height of the protuberance in respect of the inner surface of the housing varies along a width of the protuberance.
19. The heat exchanger inlet tank of claim 13 , wherein a concave indentation corresponding to the protuberance is formed on the outer surface of the housing to maintain a substantially uniform wall thickness of the inlet teak.
20. A heat exchanger, comprising:
an inlet tank including a housing having an inner surface and an outer surface and an inlet connector having an inner surface substantially continuous with the inner surface of the housing, the inner surface of the inlet connector and the inner surface of the housing converging to form an inlet interface;
a protuberance having a substantially arcuate cross-section disposed on the inner surface of the housing extending from at least a portion of the inlet interface along the inner surface of the housing to a transitional portion of the inner surface of the housing;
a concave indentation corresponding to the protuberance formed on the outer surface of the housing; and
a plurality of tubes extending from and in fluid communication with the inlet tank.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/165,779 US20150211812A1 (en) | 2014-01-28 | 2014-01-28 | Heat exchanger inlet tank with inmolded inlet radius feature |
KR1020140060373A KR101585327B1 (en) | 2014-01-28 | 2014-05-20 | Heat exchanger inlet tank with inmolded inlet radius feature |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/165,779 US20150211812A1 (en) | 2014-01-28 | 2014-01-28 | Heat exchanger inlet tank with inmolded inlet radius feature |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150211812A1 true US20150211812A1 (en) | 2015-07-30 |
Family
ID=53678709
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/165,779 Abandoned US20150211812A1 (en) | 2014-01-28 | 2014-01-28 | Heat exchanger inlet tank with inmolded inlet radius feature |
Country Status (2)
Country | Link |
---|---|
US (1) | US20150211812A1 (en) |
KR (1) | KR101585327B1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3336477A1 (en) * | 2016-12-13 | 2018-06-20 | João de Deus & Filhos, S.A. | Flow deviator in end tanks of heat exchangers for thermal stress reduction |
US20190285368A1 (en) * | 2018-03-16 | 2019-09-19 | Hamilton Sundstrand Corporation | Inlet header duct design features |
Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1921988A (en) * | 1931-04-20 | 1933-08-08 | Indian Refining Co | Heating element |
US4917180A (en) * | 1989-03-27 | 1990-04-17 | General Motors Corporation | Heat exchanger with laminated header and tank and method of manufacture |
US5117903A (en) * | 1987-07-13 | 1992-06-02 | Terumo Kabushiki Kaisha | Multitube heat exchanger with uniform-flow baffles in head chamber |
US5848639A (en) * | 1997-01-24 | 1998-12-15 | Caterpillar, Inc. | Non-metallic flow divider |
US6116335A (en) * | 1999-08-30 | 2000-09-12 | Delphi Technologies, Inc. | Fluid flow heat exchanger with reduced pressure drop |
US6997250B2 (en) * | 2003-08-01 | 2006-02-14 | Honeywell International, Inc. | Heat exchanger with flow director |
US20070062679A1 (en) * | 2005-06-30 | 2007-03-22 | Agee Keith D | Heat exchanger with modified diffuser surface |
US20070079957A1 (en) * | 2005-10-07 | 2007-04-12 | Denso Corporation | Heat exchanger |
US20070187080A1 (en) * | 2006-02-14 | 2007-08-16 | Denso Corporation | Heat exchanger |
US20080289807A1 (en) * | 2004-11-15 | 2008-11-27 | Behr Gmbh & Co. Kg | Metal Collecting Tank for a Heat Exchanger, Especially for Motor Vehicles |
US20110056654A1 (en) * | 2009-09-04 | 2011-03-10 | Vaughn James J | Heat exchanger having flow diverter and method of operating the same |
US20130025838A1 (en) * | 2010-04-23 | 2013-01-31 | Calsonic Kansei Corporation | Header tank for heat exchanger |
-
2014
- 2014-01-28 US US14/165,779 patent/US20150211812A1/en not_active Abandoned
- 2014-05-20 KR KR1020140060373A patent/KR101585327B1/en active IP Right Grant
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1921988A (en) * | 1931-04-20 | 1933-08-08 | Indian Refining Co | Heating element |
US5117903A (en) * | 1987-07-13 | 1992-06-02 | Terumo Kabushiki Kaisha | Multitube heat exchanger with uniform-flow baffles in head chamber |
US4917180A (en) * | 1989-03-27 | 1990-04-17 | General Motors Corporation | Heat exchanger with laminated header and tank and method of manufacture |
US5848639A (en) * | 1997-01-24 | 1998-12-15 | Caterpillar, Inc. | Non-metallic flow divider |
US6116335A (en) * | 1999-08-30 | 2000-09-12 | Delphi Technologies, Inc. | Fluid flow heat exchanger with reduced pressure drop |
US6997250B2 (en) * | 2003-08-01 | 2006-02-14 | Honeywell International, Inc. | Heat exchanger with flow director |
US20080289807A1 (en) * | 2004-11-15 | 2008-11-27 | Behr Gmbh & Co. Kg | Metal Collecting Tank for a Heat Exchanger, Especially for Motor Vehicles |
US20070062679A1 (en) * | 2005-06-30 | 2007-03-22 | Agee Keith D | Heat exchanger with modified diffuser surface |
US20070079957A1 (en) * | 2005-10-07 | 2007-04-12 | Denso Corporation | Heat exchanger |
US20070187080A1 (en) * | 2006-02-14 | 2007-08-16 | Denso Corporation | Heat exchanger |
US20110056654A1 (en) * | 2009-09-04 | 2011-03-10 | Vaughn James J | Heat exchanger having flow diverter and method of operating the same |
US20130025838A1 (en) * | 2010-04-23 | 2013-01-31 | Calsonic Kansei Corporation | Header tank for heat exchanger |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3336477A1 (en) * | 2016-12-13 | 2018-06-20 | João de Deus & Filhos, S.A. | Flow deviator in end tanks of heat exchangers for thermal stress reduction |
US20190285368A1 (en) * | 2018-03-16 | 2019-09-19 | Hamilton Sundstrand Corporation | Inlet header duct design features |
US10845135B2 (en) * | 2018-03-16 | 2020-11-24 | Hamilton Sundstrand Corporation | Inlet header duct design features |
US11415378B2 (en) | 2018-03-16 | 2022-08-16 | Hamilton Sundstrand Corporation | Inlet header duct design features |
Also Published As
Publication number | Publication date |
---|---|
KR101585327B1 (en) | 2016-01-13 |
KR20150089897A (en) | 2015-08-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8074708B2 (en) | Heat exchanger | |
EP3084218B1 (en) | Compressor for a vehicle air supply system | |
EP3388770B1 (en) | Heat exchanger | |
US20080164015A1 (en) | Contra-tapered tank design for cross-counterflow radiator | |
CN103925826A (en) | Tube for a heat exchanger | |
US10247490B2 (en) | Flow funneling insert and heat exchanger with flow funneling element | |
CN106996707A (en) | Inside gassing characteristics for plate fin type heat exchanger | |
US20150211812A1 (en) | Heat exchanger inlet tank with inmolded inlet radius feature | |
US20150107807A1 (en) | Heat exchanger | |
US20110030936A1 (en) | Heat Exchanging Apparatus and Method of Making Same | |
JP5709733B2 (en) | Double pipe | |
US20140166249A1 (en) | Heat exchanger tank with flow elements | |
JP3627295B2 (en) | Heat exchanger | |
CN110446903B (en) | Heat exchanger | |
KR20130065174A (en) | Heat exchanger for vehicle | |
US9383042B2 (en) | Tank and spout interface for heat exchanger and its manufacturing | |
JP2010255864A (en) | Flat tube and heat exchanger | |
US20210180888A1 (en) | Heat exchanger with varying surface roughness | |
CN105378416A (en) | Method for manufacturing a multiple manifold assembly having internal communication ports | |
US20130068435A1 (en) | In-line heat exchanger assembly and method of using | |
JPH06159955A (en) | Double tube type heat exchanger | |
US9222734B2 (en) | Heat exchanger tank groove geometry | |
KR101291027B1 (en) | An Heat Exchanger | |
US20140373960A1 (en) | Bi-channel coolant tube having crossover channels to allow coolant interaction | |
CN219754921U (en) | Hydraulic pump station |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: HALLA VISTEON CLIMATE CONTROL CORP., KOREA, REPUBL Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:GOENKA, LAKHI NANDLAL;LAPLANTE, JEFF;REEL/FRAME:032212/0765 Effective date: 20131203 |
|
AS | Assignment |
Owner name: HANON SYSTEMS, KOREA, REPUBLIC OF Free format text: CHANGE OF NAME;ASSIGNOR:HALLA VISTEON CLIMATE CONTROL CORPORATION;REEL/FRAME:037556/0690 Effective date: 20150728 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |