EP3492858B1 - Collecteur à faible perte de pression d'échangeur thermique - Google Patents

Collecteur à faible perte de pression d'échangeur thermique Download PDF

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Publication number
EP3492858B1
EP3492858B1 EP18209933.3A EP18209933A EP3492858B1 EP 3492858 B1 EP3492858 B1 EP 3492858B1 EP 18209933 A EP18209933 A EP 18209933A EP 3492858 B1 EP3492858 B1 EP 3492858B1
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EP
European Patent Office
Prior art keywords
inlet
outlet
heat exchanger
recited
passages
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.)
Active
Application number
EP18209933.3A
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German (de)
English (en)
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EP3492858A1 (fr
Inventor
Michael G. Mccaffrey
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.)
RTX Corp
Original Assignee
Raytheon Technologies Corp
Priority date (The priority date 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 date listed.)
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Publication date
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Publication of EP3492858A1 publication Critical patent/EP3492858A1/fr
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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
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0243—Header boxes having a 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
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
    • 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
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape

Definitions

  • a heat exchanger includes inlet structures that distribute flow from a circular conduit into one or many smaller flow passages.
  • High initial total pressure with the inlet manifold is desired to be maintained, with minimal loss, through the heat exchanger and out the exit manifold.
  • Flow Velocity within the relative large spaces provided by the manifold are relatively low compared to airflow velocities desired within the smaller flow passages where thermal transfer occurs.
  • Higher airflow velocities through the flow passages increase thermal transfer efficiencies.
  • Pressure losses between the conduit, manifold and the smaller flow passages can be substantial and reduce airflow velocity and thereby thermal transfer efficiencies.
  • the airflow expands into the larger space that generates further pressure losses.
  • the combined pressure losses at the inlet and the outlet reduce thermal efficiencies and require structurally larger heat exchangers to accommodate increased demands.
  • Turbine engine manufactures utilize heat exchangers throughout the engine to cool and condition airflow for cooling and other operational needs.
  • Turbine engine improvements have enabled increases in operational temperatures and pressures. The increases in temperatures and pressures improve engine efficiency but also increase demands on all engine components including heat exchangers.
  • Turbine engine manufacturers continue to seek further improvements to engine performance including improvements to thermal transfer and propulsive efficiencies.
  • EP 3 173 724 A1 discloses a prior art header for a heat exchanger.
  • a ratio between an area of the inlet and an area of the outlet of each of the plurality of splitter passages is between 1.5 and 5.
  • the inlet includes a circular shape in cross-section and is divided into passage inlets of equal area that correspond with each of the plurality of splitter passages.
  • each of the passage inlets are pie-shaped in cross-section.
  • each of the passage inlets are circular shaped in cross-section.
  • the outlet includes a rectangular shape in cross-section and is divided into passage outlets of equal area that correspond with the plurality of splitter passages.
  • each of the passage outlets is in communication with more than one of the plurality of flow passages.
  • each of the plurality of splitter passages includes a smooth curved passage without interruption between the inlet and the outlet.
  • the exhaust manifold includes an inlet portion at the second end of the plurality of flow passages and an outlet portion.
  • the exhaust manifold includes a plurality of exhaust passages defining separate flow passages between the inlet portion and the outlet portion.
  • the inlet portion is divided into a plurality of rectangular inlets corresponding with the second end of the plurality of flow passages.
  • each of the outlet portions includes a plurality of outlets having one of a pie-shaped cross-section and curvilinear shaped cross-section.
  • each of the core sections defines an area ratio between the inlet and the outlet of between 1.5 and 5.
  • the core sections define the inlet as one of a pie-shaped and a curvilinear shape in cross-section.
  • each of the core sections define a smooth curved passage without interruption between the inlet and the outlet.
  • the plurality of core sections together define a circular inlet in cross-section.
  • the core defines a substantially rectangular outlet in cross-section.
  • a disclosed heat exchanger 10 includes an intake manifold 12 and an exhaust manifold 14.
  • the intake manifold 12 is disposed on a first end 32 of a plurality of plates 16 with a limited number identified in Figure 1 .
  • the exhaust manifold 14 is disposed on a second end 34 of the plurality of plates 16.
  • the intake manifold 12 defines an inlet 26 that communicates a first flow 22 to the first end 32 of the plates 16.
  • Each of the plates 16 includes a first flow passage 18 between the first end 32 and the second end 34.
  • the plates 16 also define a second flow path 20 for cooling airflow.
  • the second flow path 20 is comprised of a plurality of fins 30 that extend upward from an outer surface of each of the plates 16.
  • Airflow 22 through the first flow passage 18 is placed in thermal contact with the cooling airflow 24 through the second flow path 20.
  • the disclosed example plate 16 comprises a single unitary part that provides for thermal communication between the inlet flow 22 and the cooling airflow 24. It should be understood that it is within the contemplation of this disclosure that other plate configurations or other heat exchanger configurations could be utilized, benefit from this disclosure, and are within the contemplation of this disclosure.
  • the airflow 22 is of a hotter temperature and flows through the first flow passage 18 defined by the plate 16. Cooled flow 36 exits through the exhaust manifold outlet 28.
  • Both the intake manifold 12 and the exhaust manifold 14 includes a plurality of separate splitter passages 38 defined within a housing 52 between an inlet that receives flow and an outlet that distributes a flow to the plurality of flow passages 18.
  • the exhaust manifold receives airflow from the first flow passage 18 defined within the plates 16 and transitions that flow into the circular outlet 28.
  • the inlet flow 22 flows through a substantially circular inlet and is divided evenly to provide a smooth uniform flow path to each of the first flow passages 18. It should be understood that although the intake manifold 12 is described by way of example in this disclosure, that the same features are also applicable to the exhaust manifold 14.
  • the example intake manifold 12 includes the inlet 26 and an outlet 40.
  • the outlet 40 distributes airflow to a plurality of first ends 32 of a corresponding plurality of the plates 16.
  • the splitter passages 38 define a flow path between the inlet 26 and the outlet 40.
  • the splitter passages 38 include smooth curved walls 50 reduce disruptions that may create turbulence and inefficient airflows.
  • Each of the splitter passages 38 include smooth walls 50 along the curved passage without interruption between the inlet 26 and outlet 40.
  • surface treatments and/or surface features 55 may be added to the smooth walls 50, to assist the turning of the flow, within the passage 38.
  • the smooth walls 50 may include surface features 55 that assist in turning of flow within the passage 38.
  • the surface features 55 may include vortex generating structures such as dimples and local areas of increased roughness relative to the smooth walls 50.
  • the surface features 55 can be utilized in regions of where flow might separate from the walls 50 and cause aerodynamic disturbances that reduce flowrate.
  • the inlet 26 is divided into a plurality of inlet portions 42 that include a cross sectional area 46.
  • the outlet 40 is divided into a plurality of outlet portions 44 that include an area 48.
  • a ratio between the inlet area 46 and the outlet area 48 is within a range between 1.5 and 5.
  • Each of the inlet portions 42 are of an equal area and disposed within the cross section of the inlet 26.
  • the disclosed exhaust manifold 14 is substantially the same as the intake manifold 12 except reversed such that airflow exiting through second ends 34 of the plurality of plates 16 enters a rectangular inlet portion and exits through the circular outlet 28.
  • the splitter passages 38 include a common flow volume between the inlet 26 and the outlet 40.
  • the exhaust manifold 14 includes exhaust passages 56 that, like passages 38, are of an equal flow area from the inlet portion to the outlet 28.
  • the inlet portion is divided into a plurality of rectangular inlets 54.
  • the outlet 28 is divided into a plurality of outlet portions 58 having a pie-shaped cross-section.
  • the outlet portions 58 may also be of other curvilinear shapes in cross-section corresponding to each of the exhaust passages 56.
  • the example inlet 26 is a circular shape in cross section and is subdivided into six separate inlet portions 42.
  • Each of the inlet portions 42 are of a substantially equal area and communicate independently with a corresponding passage 38.
  • each of the inlet portions 42 are substantially pie shaped (or sector-shaped) in cross section and subdivide the circular cross section 26 of the inlet into six separate inlet portions 42 that communicate with different corresponding splitter passages 38.
  • the example outlet 40 includes a plurality of outlet portions 44 that are substantially rectangular.
  • the rectangular orientation and cross sectional shape matches the inlet shape for the plate 16. It should be appreciated that other shapes of the outlet openings 44 could be utilized to correspond with shapes of the inlets to each of the plates 16. Moreover, it should be understood that each of the outlet portions 44 correspond with in at least one or several of the flow passages 18.
  • FIG. 10 another example inlet 25 is shown and includes a plurality of inlet portions 41.
  • the inlet 25 includes a circular cross section and includes a plurality of subdivided inlet portions 41.
  • Each of the inlet portions 41 is a curvilinear shape that includes an irregularly curved shape. The different curvilinear shapes are provided to fit within the circular cross section of the inlet 25.
  • example inlet portions 41 are schematically shown, other regular and irregularly shaped inlet portions 41 could be utilized and are within the contemplation of this disclosure.
  • the inlet portions 41 are substantially identical in area while not identical in shape and provide smoothed shape to transition into each corresponding splitter passages 38.
  • another example inlet 27 is substantially circular and divided into rectangular inlet portions 43.
  • Each of the rectangular inlet portions 43 correspond with one of the corresponding splitter passages 38.
  • FIG. 12 another example intake manifold 60 is shown and includes an inlet 62 that is subdivided into different inlet portions 66.
  • the manifold 60 includes a housing 68 that defines a plurality of separate passages 74 that extend from the inlet 62 to the outlet 64.
  • the passages 74 define a single unitary smoothly curved passage that reduces pressure losses.
  • the inlet 62 includes separate inlet portions 66 and the outlet 64 includes separate outlet portions 72.
  • the example housing 68 including the inlet 62 and the outlet 64 is a single unitary structure without seams or joints between different portions.
  • the outlet 64 includes flanges 70.
  • the flanges 70 are attached to the intake manifold 60 and enable securement to the plates 16 or to supporting structures utilized to support the heat exchanger 60 in operation.
  • the flanges 70 are shown as a separate feature from the housing 68, but also may be an integrally formed as a portion of the housing 68.
  • a method of creating one of the disclosed manifolds 12, 14 and 60 includes a casting operation where a core assembly 76 is utilized to define each of the individual flow splitter passages 38 ( Figure 4 ).
  • the core assembly 76 includes a plurality of passage defining structures 78A-F.
  • Each of the passage defining structures 78A-F includes an inlet portion 80A-F and an outlet portion 82A-F.
  • the core assembly 76 is inserted into a mold 84 that defines a cavity 86.
  • the cavity 86 defines outer surface features of a completed intake manifold.
  • a casting material 88 is injected into the mold 84 and filled around the core assembly 76 to define the completed part.
  • the cast part is then removed from the mold 84.
  • the core assembly 76 is than removed according to known procedure and processes to provide a completed intake manifold 90. Additional finishing steps may be required to finalize the intake manifold 90 such as for example, polishing, machining, coating and other finishing processes as are known. Additionally, flange 70 may be added if not part of the cast manifold 90.
  • the example disclosed manifolds includes features to limit pressure losses and improve thermal transfer efficiencies. Moreover, each of the manifolds includes features that enable airflow velocities to be increased to improve thermal transfer efficiencies.

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  • 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)

Claims (15)

  1. Échangeur thermique (10) comprenant :
    une pluralité de passages d'écoulement (18) en contact thermique avec un écoulement de refroidissement (24), la pluralité de passages d'écoulement (18) comportant une première extrémité (32) et une seconde extrémité (34) ;
    un collecteur d'admission (12 ; 60) à la première extrémité (32) de la pluralité de passages d'écoulement (18), le collecteur d'admission (12 ; 60) comportant une pluralité de passages de séparation indépendants (38 ; 74) qui communiquent le flux d'air (22) à la première extrémité (32) de la pluralité de passages d'écoulement (18) ; et
    un collecteur d'échappement (14) à la seconde extrémité (34) de la pluralité de passages d'écoulement (18), caractérisé en ce que
    chacun de la pluralité de passages de séparation indépendants (38 ; 74) comporte un volume d'écoulement entre une entrée (25 ; 26 ; 27 ; 62) du collecteur d'admission (12 ; 60) et une sortie (40 ; 64) du collecteur d'admission (12 ; 60) dans la première extrémité (32) de la pluralité de passages (18) qui est identique.
  2. Échangeur thermique (10) selon la revendication 1, dans lequel un rapport entre une surface (46) de l'entrée (25 ; 26 ; 27 ; 62) et une surface (48) d'une sortie (44) de chacun de la pluralité de passages de séparation (38 ; 74) est compris entre 1,5 et 5.
  3. Échangeur thermique (10) selon la revendication 1 ou 2, dans lequel l'entrée (25 ; 26 ; 27 ; 62) comprend une section transversale de forme circulaire et est divisée en entrées de passage (41 ; 42 ; 43) de surface égale qui correspondent à chacun de la pluralité de passages de séparation (38 ; 74).
  4. Échangeur thermique (10) selon la revendication 3, dans lequel chacune des entrées de passage (41 ; 42 ; 43) a une section transversale en forme de tarte ou de forme curviligne.
  5. Échangeur thermique (10) selon une quelconque revendication précédente, dans lequel la sortie (40 ; 64) comprend une section transversale de forme rectangulaire et est divisée en sorties de passage (44 ; 72) de surface égale qui correspondent à la pluralité de passages de séparation (38 ; 74).
  6. Échangeur thermique (10) selon la revendication 5, dans lequel chacune des sorties de passage (44 ; 72) est en communication avec plus d'un de la pluralité de passages d'écoulement (18).
  7. Échangeur thermique (10) selon une quelconque revendication précédente, dans lequel chacun de la pluralité de passages de séparation (38 ; 74) comprend un passage incurvé lisse (50) sans interruption entre l'entrée (25 ; 26 ; 27 ; 62) et la sortie (40; 64).
  8. Échangeur thermique (10) selon une quelconque revendication précédente, dans lequel le collecteur d'échappement (14) comporte une partie d'entrée à la seconde extrémité (34) de la pluralité de passages d'écoulement (18) et une partie de sortie (28), et le collecteur d'échappement (14) comporte une pluralité de passages d'échappement (56) entre la partie d'entrée et la partie de sortie (28).
  9. Échangeur thermique (10) selon la revendication 8, dans lequel la partie d'entrée est divisée en une pluralité d'entrées rectangulaires (54) correspondant à la seconde extrémité (34) de la pluralité de passages d'écoulement (18).
  10. Échangeur thermique (10) selon la revendication 8 ou 9, dans lequel la partie de sortie (28) comprend une pluralité de sorties (58) ayant une section transversale en forme de tarte ou une section transversale de forme curviligne.
  11. Procédé de formation d'un collecteur (12 ; 14 ; 60) pour un échangeur thermique (10) selon la revendication 1, le procédé comprenant les étapes suivantes :
    la création d'une pluralité de sections de noyau (78A-F) qui définissent un passage (38 ; 56 ; 74) entre une entrée (25 ; 26 ; 27 ; 62) et une sortie (28 ; 40 ; 64), dans lequel une zone d'entrée pour chacune de la pluralité de sections de noyau (78A-F) est identique, une zone de sortie pour chacune de la pluralité de sections de noyau (78A-F) est identique, et le volume d'écoulement entre la zone d'entrée et la zone de sortie pour chacune de la pluralité de sections de noyau (78A-F) est identique ;
    la définition d'un moule (84) avec une cavité de moule (86) pour recevoir les sections de noyau (78A-F) qui définissent une forme extérieure du collecteur (12 ; 14 ; 60) ;
    le moulage de la pluralité de sections de noyau (78A-F) à l'intérieur de la cavité de moule (86) pour enfermer les sections de noyau (78A-F) à l'intérieur d'un matériau de moulage (88) ; dans lequel le matériau de moulage (88) est injecté dans le moule (84) ; et
    le retrait des sections de noyau (78A-F) du matériau de moulage (88).
  12. Procédé selon la revendication 11, dans lequel chacune des sections de noyau (78A-F) définit un rapport de surface entre l'entrée (25 ; 26 ; 27 ; 62) et la sortie (28 ; 40 ; 64) compris entre 1,5 et 5.
  13. Procédé selon la revendication 11 ou 12, dans lequel les sections de noyau (78A-F) définissent l'entrée (25 ; 26 ; 27 ; 62) comme ayant une section transversale en forme de tarte ou de forme curviligne.
  14. Procédé selon l'une quelconque des revendications 11 à 13, dans lequel chacune des sections de noyau (78A-F) définit un passage incurvé lisse (50) sans interruption entre l'entrée (25 ; 26 ; 27 ; 62) et la sortie (28 ; 40 ; 64).
  15. Procédé selon l'une quelconque des revendications 11 à 14, dans lequel :
    la pluralité de sections de noyau (78A-F) définissent ensemble une entrée circulaire (25 ; 26 ; 27 ; 62) en section transversale ; et/ou
    la pluralité de sections de noyau (78A-F) définissent ensemble une sortie sensiblement rectangulaire en section transversale.
EP18209933.3A 2017-12-01 2018-12-03 Collecteur à faible perte de pression d'échangeur thermique Active EP3492858B1 (fr)

Applications Claiming Priority (1)

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US201762593413P 2017-12-01 2017-12-01

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EP3492858B1 true EP3492858B1 (fr) 2022-02-16

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10545001B2 (en) * 2016-01-21 2020-01-28 Hamilton Sundstrand Corporation Heat exchanger with adjacent inlets and outlets
EP3992565B1 (fr) * 2020-10-28 2024-03-13 B/E Aerospace, Inc. Collecteur d'échangeur de chaleur

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US673767A (en) * 1900-04-10 1901-05-07 Mary J Eycleshymer Steam-radiator.
US5894649A (en) * 1997-08-28 1999-04-20 Transpro, Inc. Heat exchanger assembly utilizing grommets and integral cast tanks
JP2005077012A (ja) * 2003-09-01 2005-03-24 Nissan Motor Co Ltd ラジエータ
DE102008006474A1 (de) * 2008-01-29 2009-07-30 Modine Manufacturing Co., Racine Wärmetauscher
JP2011133198A (ja) * 2009-12-25 2011-07-07 Tokyo Radiator Mfg Co Ltd 車両用インタークーラ
US20170146305A1 (en) * 2015-11-24 2017-05-25 Hamilton Sundstrand Corporation Header for heat exchanger
US20170211896A1 (en) * 2016-01-21 2017-07-27 Hamilton Sundstrand Corporation Heat exchanger with center manifold

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EP3492858A1 (fr) 2019-06-05

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