US20150362264A1 - Flow deflector - Google Patents

Flow deflector Download PDF

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Publication number
US20150362264A1
US20150362264A1 US14/741,571 US201514741571A US2015362264A1 US 20150362264 A1 US20150362264 A1 US 20150362264A1 US 201514741571 A US201514741571 A US 201514741571A US 2015362264 A1 US2015362264 A1 US 2015362264A1
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United States
Prior art keywords
tubes
bundle
shell
tubular body
flow deflector
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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
Application number
US14/741,571
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English (en)
Inventor
José Antonio Grande Fernandez
Marcos Rodríguez Tato
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Emissions Systems Spain SL
Original Assignee
BorgWarner Emissions Systems Spain SL
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Filing date
Publication date
Application filed by BorgWarner Emissions Systems Spain SL filed Critical BorgWarner Emissions Systems Spain SL
Assigned to BORGWARNER EMISSIONS SYSTEMS SPAIN, S.L.U. reassignment BORGWARNER EMISSIONS SYSTEMS SPAIN, S.L.U. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RODRIGUEZ TATO, MARCOS, GRANDE FERNANDEZ, JOSE ANTONIO
Publication of US20150362264A1 publication Critical patent/US20150362264A1/en
Abandoned legal-status Critical Current

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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
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/10—Safety or protection arrangements; Arrangements for preventing malfunction for preventing overheating, e.g. heat shields

Definitions

  • the present invention relates to a device for deflecting coolant fluid flow in a heat exchanger, particularly a heat exchanger of an EGR (Exhaust Gas Recirculation) system, better cooling of the fluid to be cooled and flowing through the bundle of tubes of said heat exchanger being obtained.
  • EGR exhaust Gas Recirculation
  • Heat exchangers comprise bundles of tubes which are housed in a shell, and a flow channel of a first fluid, the coolant fluid, is generated in the space existing between said tubes and the shell.
  • the ratio of space existing between the shell and the tubes to space existing between the tubes themselves is relevant for first coolant fluid flow which tends to flow through said first space located between the shell and the tubes as there is less resistance, cooling efficiency being reduced.
  • heat exchangers comprising floating cores where the bundle of tubes comprises an element in at least one of its ends allowing the longitudinal displacement necessary to compensate for differential thermal expansion between the core and the shell, such that said expansions do not generate stress.
  • the present invention proposes a solution to the preceding problems by means of a flow deflection system.
  • a first inventive aspect provides a flow deflector adapted for being installed in heat exchangers of the type comprising a shell with an inner chamber through which a first coolant fluid circulates and where said shell houses at least a bundle of tubes through which a second fluid to be cooled circulates, where between the bundle of tubes and the wall of the inner chamber of the shell there is a perimetral gap in at least one section of the length of the bundle of tubes.
  • the deflector according to this first inventive aspect comprises:
  • tubular body adapted for surrounding at least one section of the length of the bundle of tubes
  • first expansion section arranged at one end of the tubular body such that the tubular body is extended longitudinally by means of the first expansion section
  • the first expansion section covers a larger perimeter than the perimeter covered by the tubular body to reduce the perimetral gap between the bundle of tubes and the wall of the inner chamber of the shell;
  • the heat exchanger has a floating core, a space must be provided between the tubes of the bundle of tubes and the inner wall of the shell, or inner chamber, for mounting same.
  • the space existing between the tubes of the bundle of tubes and the inner wall of the shell is defined as perimetral gap, whereas the space defined between the actual tubes of the bundle of tubes is referred to as inner space.
  • the first fluid i.e., the coolant fluid
  • the first fluid tends to circulate through the spaces offering less resistance, or in other words, where the section of the passage is larger.
  • the first fluid preferably runs through the channel defined between the bundle of tubes and the inner wall of the shell, or perimetral gap, such that the flow rate of the first fluid intended for flowing through the space located between the tubes of the bundle of tubes, i.e., the inner space, is reduced, and heat is removed by convection.
  • said heat exchanger has a perimetral gap between the inner wall of the shell and the tubes of the bundle of tubes in at least one section of the length of said tubes.
  • Said perimetral gap allows mounting a floating core. Nevertheless, this perimetral gap generates a flow channel around the bundle of tubes for the first fluid different from the flow channel between the tubes of the bundle of tubes, or inner space, through which said first fluid must circulate.
  • the flow deflector of the present invention allows minimizing the first coolant fluid flow rate through the first channel established through the perimetral gap located between the bundle of tubes and the inner wall of the shell.
  • the deflector according to the first inventive aspect is adapted for restricting first fluid passage through the flow channel located in the perimetral gap, such that the flow is redirected towards the channel formed by the inner space. Therefore, the increase in flow rate through the channel formed by the inner space also causes an increase in speed, reducing the stagnant regions and therefore the occurrence of possible hot spots.
  • the present flow deflector comprises a tubular body which is located surrounding a plurality of tubes of the bundle of tubes, preferably all of said bundle of tubes. This tubular body is extended in at least a longitudinal section of the tubes of the surrounded bundle of tubes.
  • the tubular body defines a perimetral flow barrier the section of which can vary along the length of extension thereof such that once driven to the inner space, the fluid can no longer access the perimetral gap except for minimal leaks that may occur in areas where parts are attached to one another, for example.
  • the flow deflector of the present invention further comprises a first expansion section located at one of the ends of the tubular body in the preferred example.
  • This first expansion section defines a larger perimeter than the largest perimeter defined by the tubular body.
  • the perimetral gap defined between the bundle of tubes and the inner wall of the shell is smaller in the area where the first expansion section is located than along the length covered by the tubular body.
  • the first expansion section is located against the inner wall of the shell to prevent fluid passage through the perimetral gap.
  • the transition between the first expansion section and the tubular body establishes a first coolant fluid flow passage restriction, such that the first coolant fluid is forced to circulate through the inner space.
  • the first expansion section therefore acts as an inlet for the first coolant fluid which is collected by the area having a larger perimeter and forced to be introduced into the inner space.
  • the flow deflector defined in the first inventive aspect concentrates the first coolant fluid in the space defined between the tubes of the bundle of tubes, i.e., it increases the first coolant fluid flow directed towards the bundle of tubes, such that cooling efficiency in said tubes increases.
  • the flow deflector allows the heat exchanger to require a smaller amount of coolant since it improves the proportion of the amount of first coolant fluid intended for contacting with the outer surface of the tubes, removing heat by convection.
  • the incorporation of the deflector according to the first inventive aspect allows using lower first fluid flow rates, maintaining heat exchanger efficiency.
  • the part of the flow circulating through the perimetral gap reduces the flow circulating through the inner space, and to compensate for the reduction of discharged heat it is necessary to increase the total coolant fluid flow rate. For this reason, it is indicated that it is possible to reduce the first fluid flow rate in comparison with the exchanger without using the deflector according to the invention.
  • the present deflector allows being used in heat exchangers with a floating core without hindering mounting due to the placement thereof on the tubes of the bundle of tubes of the tubular body and to the fact that it is not attached to the shell. This means that it does not restrict differential movement between the shell and the tubes of the bundle of tubes, so it does not interfere with the operation or the mounting of any type of core, be it a floating core or a rigid core.
  • the flow deflector has a tubular body comprising a second expansion section located at the end of the tubular body opposite to the end where the first expansion section is located.
  • a second expansion section in the deflector advantageously allows an oriented exit of the first coolant fluid.
  • This second expansion section acts a funnel allowing the exit of the first fluid flow, preventing it from flowing back, creating recirculation areas, and from accessing the perimetral gap existing between the inside of the shell and the tubular body, surrounding the bundle of tubes.
  • the flow deflector presents at least one elastically deformable expansion section to assure support against the wall of the inner chamber of the shell.
  • This feature in at least one of the expansion sections allows supporting the flow deflector on the inner chamber of the shell. This advantageously reduces vibrations suffered by the bundle of tubes or at least causes a node in the vibration modes increasing the natural vibration frequency, reducing the probability of fatigue damage since the amplitude of core oscillations is reduced.
  • the flow deflector presents a curved section in the region in at least one of the expansion sections which is adapted for contacting with the wall of the inner chamber of the shell to prevent wedging.
  • This curved section in at least one of the expansion sections assures robuster support on the wall of the inner chamber of the shell.
  • the flow deflector presents in the second expansion section at least one window to favor coolant fluid passage, both the entry and exit of said coolant fluid, between the inner space and the perimetral gap.
  • the flow deflector presents a window that is prolonged along a region of the tubular body.
  • the entry or exit of the first coolant fluid to/from the heat exchanger is established through the shell in most embodiments.
  • the entry or exit of the flow restricted by means of the tubular body through a window is faster than through the tubes of the bundle of tubes along the entire tubular body of the deflector given that it allows the flow to have a path with less resistance.
  • the flow deflector presents perimetral expansions in the tubular body for housing baffles of the bundle of tubes.
  • Said perimetral expansions are sections along the tubular body where the perimeter, according to a section transverse to the longitudinal direction defined by the bundle of tubes, is greater than the perimeter defined by the tubular body, and less than or equal to the perimeter defined by the expansion section.
  • the perimetral expansions advantageously allow housing flow deflector baffles located in the space between the tubes of the bundle of tubes. Said baffles guide the first coolant fluid flow according to a specific path inside the flow channel defined between the tubes of the bundle of tubes, assure the separation between the tubes and provide greater structural rigidity.
  • the perimetral expansions advantageously provide axial retention of the flow deflector with respect to the tubes of the bundle of tubes, given that the baffles housed therein are fixed in the tubes of the bundle of tubes and the deflector is not attached by welding or by equivalent attachment means to any element of the exchanger.
  • the flow deflector is made of die-cut and pressed sheet metal. This means that the process for manufacturing said deflector is a simple and low-cost process due to the simplicity of the operations necessary both for manufacture and for subsequent assembly in the operating position.
  • the flow deflector presents elastically deformable expansion sections configured by means of longitudinal grooves making the deformation thereof easier by increasing flexibility.
  • Longitudinal groove is understood as a groove extending according to the direction indicated by the longitudinal direction defined by the bundle of tubes.
  • the expansion section can be configured with a curvature for being located against the inner wall of the shell without causing wedging.
  • the groove is considered to be showing a longitudinal direction, even in this curved configuration, if the plane containing it is parallel to the longitudinal axis of the bundle of tubes. This will be the case of the embodiments described below.
  • the longitudinal grooves allow the expansion sections to undergo greater deformation without negatively affecting the support they provide when contacting with the wall of the inner chamber of the shell.
  • the sheet sections located between grooves contact with the wall, forcing the deformation thereof by bending such that they move closer to one another, the space formed by the grooves being reduced and assimilating the configuration that an expansion section without longitudinal grooves would have. Due to the deformation adopted by the sections located between grooves after insertion, this final configuration prevents the flow passage through the grooves since they are closed.
  • This configuration advantageously means that the expansion sections with longitudinal grooves allow supporting the flow deflector against the wall of the inner chamber of the shell, thus reducing vibrations suffered by the bundle of tubes.
  • This vibration damping is more efficient with longitudinal grooves given that they are more flexible and allow greater deformation.
  • the flow deflector is configured in two or more portions attached to one another by clipping.
  • the deflector is configured in two portions such that both portions enclose the bundle of tubes therein such that said portions are located in opposition.
  • the different portions allow better adjustment in the position thereof to then be attached to one another through any attachment method allowing the parts to have no relative movement between them.
  • the different parts are coupled to one another such that they are fixed together once the attachment is performed.
  • Said attachment is preferably performed by clipping such that the portions of the flow deflector are provided both with flanges and housings for said flanges, allowing solid and at the same time removable anchoring of the attached parts forming the flow deflector.
  • Another object of this invention is the heat exchanger comprising the deflector, the heat exchanger particularly comprising:
  • a core comprising at least one bundle of tubes through which a second fluid to be cooled circulates where said shell houses the at least one bundle of tubes, and where between the bundle of tubes and the wall of the inner chamber of the shell, there is a perimetral gap in at least one section of the length of the bundle of tubes,
  • a deflector according to the first inventive aspect located in the perimetral gap.
  • a heat exchanger having these features advantageously allows more efficient cooling of the second fluid, given that it forces the first fluid to pass through the inside of the tubes of the bundle of tubes and prevents said first fluid from looking for paths through the space between the bundle of tubes and the shell, or perimetral gap.
  • the cooling is more efficient and can be obtained with a smaller amount of first coolant fluid than in a heat exchanger that does not contain at least one flow deflector of this type.
  • FIG. 1 shows a perspective view of a heat exchanger with a flow deflector according to an embodiment of the invention.
  • FIG. 2 shows an exploded view of all the components of a heat exchanger such as that of the preceding figure.
  • FIG. 3 a shows a plan view of a section according to a plane cutting through the shell but not the deflector of the heat exchanger shown in FIG. 1 with all its components.
  • FIG. 3 b shows an elevational view of a section according to a plane cutting through the shell but not the deflector of the heat exchanger shown in FIG. 1 with all its components.
  • FIG. 4 a shows an elevational view of a portion configuring the flow deflector through the attachment of two of these portions.
  • FIG. 4 b shows a plan view of the same portion of the flow deflector.
  • FIG. 4 c shows a side view of the same portion of the flow deflector.
  • the present invention relates to a device for deflecting a first coolant fluid flow circulating through a heat exchanger.
  • FIG. 1 shows a heat exchanger with a floating core, comprising a flow deflector ( 3 ) such as that of the present invention.
  • Said heat exchanger comprises a core ( 2 ) formed by a bundle ( 2 . 1 ) of tubes, in this case planar tubes, a fixing baffle ( 2 . 2 ) located at one end of the bundle ( 2 . 1 ) of tubes of said core ( 2 ), and a bushing ( 2 . 3 ) located at the opposite end suitable for the floating attachment of the core ( 2 ).
  • the bundle ( 2 . 1 ) of tubes is fixed to the fixing baffle ( 2 . 2 ), such that movement due to longitudinal expansion with respect to the shell ( 1 ) housing the bundle ( 2 . 1 ) of tubes is allowed at the end of the bushing ( 2 . 3 ) to reduce the thermal fatigue of the device during operation.
  • the flow deflector ( 3 ) is formed by two portions attached to one another by means of clipping through an assembly of flanges ( 3 . 6 ) on each side.
  • the flow deflector ( 3 ) has a tubular body ( 3 . 1 ) extending along a portion of the length of the bundle ( 2 . 1 ) of tubes, completely surrounding the tubes forming said bundle ( 2 . 1 ) of tubes.
  • the flow deflector ( 3 ) comprises at its ends a first expansion section ( 3 . 2 ) and a second expansion section ( 3 . 3 ), having a larger perimeter than the tubular body ( 3 . 1 ) and in which a series of longitudinal grooves ( 3 . 2 . 1 , 3 . 3 . 1 ) are machined.
  • the portions giving rise to the deflector ( 3 ) are manufactured in die-cut and pressed sheet metal.
  • the longitudinal grooves ( 3 . 2 . 1 , 3 . 3 . 1 ) are obtained in these same die-cutting operations.
  • the main function of the first expansion section ( 3 . 2 ) and the second expansion section ( 3 . 3 ) is to act as a funnel, directing the directed entry and exit of most of the first coolant fluid flow through the flow channel formed by the space comprised between the tubes of the bundle ( 2 . 1 ) of tubes, or inner space, preventing part of said flow from going through the space existing between the bundle ( 2 . 1 ) of tubes and the shell ( 1 ), or perimetral gap.
  • the expression “most of the flow” is used since there may be small clearances or, as can be seen below, grooves ( 3 . 2 . 1 , 3 . 3 . 1 ) which allow certain portions of the deflector to bend, giving rise to small amounts of flow compared with the main flow without these minor flows preventing the increase in heat exchanger efficiency.
  • the flow deflector ( 3 ) also comprises a window ( 3 . 4 ) located at one of its ends, both on the tubular body ( 3 . 1 ) and on one of the expansion sections ( 3 . 2 , 3 . 3 ).
  • the flow deflector ( 3 ) also comprises a plurality of perimetral expansions ( 3 . 5 ) allowing both axially fixing the flow deflector ( 3 ), and housing a series of baffles ( 2 . 1 . 1 ) integral with the bundle ( 2 . 1 ) of tubes, which are in turn flow deflectors inside the channel formed between the tubes of the bundle ( 2 . 1 ) of tubes, or inner space.
  • FIG. 2 shows a heat exchanger according to an exploded view with all its elements together with a flow deflector ( 3 ) such as that of the present invention.
  • FIGS. 3 a and 3 b show a section view of the shell ( 1 ) of the heat exchanger together with its inner chamber (H).
  • the core ( 2 ) and the distribution of all its elements are also shown.
  • the bundle ( 2 . 1 ) of tubes comprises a plurality of planar tubes which are attached at one of their ends to the fixing baffle ( 2 . 2 ), whereas their other end is attached to the bushing ( 2 . 3 ) allowing thermal expansion, and therefore enabling longitudinal movement of the tubes of the bundle ( 2 . 1 ) of tubes.
  • the core ( 2 ) also has baffles ( 2 . 1 . 1 ) with holes in their entire longitudinal extension or only in part of said longitudinal extension, allowing said baffles ( 2 . 1 . 1 ) to be inserted in the tubes of the bundle ( 2 . 1 ) of tubes.
  • These baffles ( 2 . 1 . 1 ) have regions for passage located alternately according to a transverse direction such that they modify the path of the first coolant fluid flow when such coolant fluid circulates through the channel defined between the tubes, or inner space.
  • a flow deflector ( 3 ) is also shown, formed in this case by two portions attached to one another by means of clipping as seen in FIG. 1 as well.
  • This flow deflector ( 3 ) comprises at least as many perimetral expansions ( 3 . 5 ) as baffles ( 2 . 1 . 1 ) comprised in the core ( 2 ), where each of the expansions ( 3 . 5 ) houses the perimetral projection of each of the baffles ( 2 . 1 . 1 ).
  • FIG. 3 a shows a plan view of a heat exchanger such as that of the preceding figures, already mounted.
  • Said plan view is a section of the shell to allow observing the mounted system therein, and in which the main portions of said shell ( 1 ), such as the main body ( 1 . 1 ) of the shell, comprising the inner chamber (H) and therefore the bundle ( 2 . 1 ) of tubes, and a cover flange ( 1 . 2 ), are distinguished.
  • Said flange ( 1 . 2 ) in contact with the fixing baffle ( 2 . 2 ), prevents the first coolant fluid from leaking out of the heat exchanger, in addition to keeping both the fixing baffle ( 2 . 2 ) and the corresponding end of the bundle ( 2 . 1 ) of tubes fixed in place.
  • FIG. 3 b shows an elevational view of a heat exchanger such as that of the preceding figures, already mounted.
  • Said elevational view is a cut through the shell to allow observing the inside of the mounted system, like in FIG. 3 a , and in which the main portions of said shell ( 1 ), such as the main body ( 1 . 1 ) of the shell, comprising the inner chamber (H) and therefore the bundle ( 2 . 1 ) of tubes, and the cover flange ( 1 . 2 ), are distinguished.
  • This figure shows the flow deflector ( 3 ) formed by two portions, already mounted and attached by means of the flanges ( 3 . 6 ) and the corresponding housings, giving rise to a clipped attachment.
  • FIGS. 4 a - 4 c show different views of one of the portions of the flow deflector ( 3 ).
  • a flow deflector ( 3 ) is mounted by combining two of these portions. The combination is possible since the flanges ( 3 . 6 ) and the housings holding these flanges ( 3 . 6 ) are positioned such that when two equal parts or portions are coupled to one another, the flanges ( 3 . 6 ) enter the corresponding housings.
  • FIG. 4 a is an elevational view of the flow deflector ( 3 ) in which are distinguished both the tubular body ( 3 . 1 ) and the perimetral expansions ( 3 . 5 ) housing the baffles ( 2 . 1 . 1 ) which, in operating position, will coincide with one another according to the longitudinal direction defined by the bundle ( 2 . 1 ) of tubes.
  • the flanges ( 3 . 6 ) that allow clipping are also distinguished.
  • Said flanges ( 3 . 6 ) also have an assembly of projections that are coupled in the housings of the opposite portion and serve to keep said portions firmly attached.
  • FIG. 4 b shows the plan view of the flow deflector ( 3 ), both the expansion sections ( 3 . 2 , 3 . 3 ) and, like in the preceding figure, the perimetral expansions ( 3 . 5 ) being distinguished.
  • the window ( 3 . 4 ) made on the tubular body ( 3 . 1 ) and on the second expansion section ( 3 . 3 ) is also shown.
  • This window ( 3 . 4 ) is configured so that it is positioned in the region for accessing the inlet or outlet conduit ( 1 . 3 , 1 . 4 ) of the first coolant fluid located in the shell ( 1 ) once the deflector ( 3 ) is mounted in the operating position on the bundle ( 2 . 1 ) of tubes.
  • the expansion sections ( 3 . 2 , 3 . 3 ) are formed according to a curved section and have longitudinal grooves ( 3 . 2 . 1 , 3 . 3 . 1 ) obtained when die-cutting, for example, leaving between them elastically deformable sections adapted for bending.
  • the deformation of the elastically deformable sections caused by the force exerted by the inner wall of the shell ( 1 ) gives rise to a configuration in which the expansion sections ( 3 . 2 , 3 . 3 ) have grooves ( 3 . 2 . 1 , 3 . 3 . 1 ) that are closed or closed to a greater extent such that the possible leak flow passage through these chinks is reduced.
  • the width of the grooves ( 3 . 2 . 1 , 3 . 3 . 1 ) is such that the elastically deformable sections adopt a closed configuration after the deformation caused by the shell ( 1 ), i.e., is reduced to not allow passage therethrough with the exception of positioning errors due to irregularities of the inner wall of the shell ( 1 ) or variations in the way of being deformed due to mounting.
  • FIG. 4 c shows a side view of the flow deflector ( 3 ) where the curved section of the first expansion section ( 3 . 2 ) is also seen together with its longitudinal grooves ( 3 . 2 . 1 , 3 . 3 . 1 ).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US14/741,571 2014-06-17 2015-06-17 Flow deflector Abandoned US20150362264A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14382234.4A EP2957852B1 (fr) 2014-06-17 2014-06-17 Déflecteurs d'écoulement
EP14382234.4 2014-06-17

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Publication Number Publication Date
US20150362264A1 true US20150362264A1 (en) 2015-12-17

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US14/741,571 Abandoned US20150362264A1 (en) 2014-06-17 2015-06-17 Flow deflector

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US (1) US20150362264A1 (fr)
EP (1) EP2957852B1 (fr)
KR (1) KR20150144723A (fr)
CN (1) CN105202965A (fr)
BR (1) BR102015014389A2 (fr)

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DE102016011254A1 (de) 2016-09-20 2018-03-22 Modine Manufacturing Company Bypass-Blockiervorrichtung für Wärmeübertrager
CN109154478A (zh) * 2016-03-14 2019-01-04 法雷奥热力股份有限公司 用于气体、特别是用于发动机废气的热交换器
US11384717B2 (en) * 2018-12-05 2022-07-12 Valeo Termico, S.A. Heat exchanger for gases, in particular engine exhaust gases

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* Cited by examiner, † Cited by third party
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DE102017218254A1 (de) * 2017-10-12 2019-04-18 Mahle International Gmbh Abgaswärmeübertrager
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EP2957852B1 (fr) 2018-12-05
KR20150144723A (ko) 2015-12-28
EP2957852A1 (fr) 2015-12-23
CN105202965A (zh) 2015-12-30

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