US20200284519A1 - Cyllindrical helical core geometry for heat exchanger - Google Patents

Cyllindrical helical core geometry for heat exchanger Download PDF

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Publication number
US20200284519A1
US20200284519A1 US16/711,126 US201916711126A US2020284519A1 US 20200284519 A1 US20200284519 A1 US 20200284519A1 US 201916711126 A US201916711126 A US 201916711126A US 2020284519 A1 US2020284519 A1 US 2020284519A1
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United States
Prior art keywords
fluid
heat exchanger
helical
inlet
outlet
Prior art date
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Abandoned
Application number
US16/711,126
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English (en)
Inventor
Ahmet T. Becene
Gabriel Ruiz
Feng Feng
Michael Maynard
Michael Doe
Michele Hu
Ephraim Joseph
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.)
Hamilton Sundstrand Corp
Original Assignee
Hamilton Sundstrand 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.)
Filing date
Publication date
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Priority to US16/711,126 priority Critical patent/US20200284519A1/en
Assigned to HAMILTON SUNDSTRAND CORPORATION reassignment HAMILTON SUNDSTRAND CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BECENE, AHMET T., DOE, MICHAEL, MAYNARD, MICHAEL, FENG, FENG, HU, MICHELE, JOSEPH, EPHRAIM, RUIZ, Gabriel
Publication of US20200284519A1 publication Critical patent/US20200284519A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0472—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 bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B33—ADDITIVE MANUFACTURING TECHNOLOGY
    • B33Y—ADDITIVE MANUFACTURING, i.e. MANUFACTURING OF THREE-DIMENSIONAL [3-D] OBJECTS BY ADDITIVE DEPOSITION, ADDITIVE AGGLOMERATION OR ADDITIVE LAYERING, e.g. BY 3-D PRINTING, STEREOLITHOGRAPHY OR SELECTIVE LASER SINTERING
    • B33Y10/00—Processes of additive manufacturing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B33—ADDITIVE MANUFACTURING TECHNOLOGY
    • B33Y—ADDITIVE MANUFACTURING, i.e. MANUFACTURING OF THREE-DIMENSIONAL [3-D] OBJECTS BY ADDITIVE DEPOSITION, ADDITIVE AGGLOMERATION OR ADDITIVE LAYERING, e.g. BY 3-D PRINTING, STEREOLITHOGRAPHY OR SELECTIVE LASER SINTERING
    • B33Y80/00—Products made by additive manufacturing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/12—Cooling of plants
    • F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/50—Building or constructing in particular ways
    • F05D2230/53—Building or constructing in particular ways by integrally manufacturing a component, e.g. by milling from a billet or one piece construction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/20—Three-dimensional
    • F05D2250/25—Three-dimensional helical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/20—Heat transfer, e.g. cooling
    • F05D2260/213—Heat transfer, e.g. cooling by the provision of a heat exchanger within the cooling circuit
    • 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
    • F28D2021/0026—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for combustion engines, e.g. for gas turbines or for Stirling engines
    • 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
    • F28D7/02—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 helically coiled
    • F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements
    • 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
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements
    • 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
    • F28F2265/30—Safety or protection arrangements; Arrangements for preventing malfunction for preventing vibrations
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft

Definitions

  • the present disclosure is related generally to heat exchangers and more particularly to heat exchanger core designs.
  • Heat exchangers can provide a compact, low-weight, and highly effective means of exchanging heat from a hot fluid to a cold fluid.
  • Heat exchangers that operate at elevated temperatures such as those used in modern aircraft engines, often have short service lifetimes due to thermal stresses, which can cause expansion and cracking of the fluid conduits.
  • Thermal stresses can be caused by mismatched temperature distribution, component stiffness, geometry discontinuity, and material properties (e.g., thermal expansion coefficients and modulus), with regions of highest thermal stress generally located at the interface of the heat exchanger inlet/outlet and core.
  • the present disclosure is directed toward a heat exchanger that includes a tubular inlet, a tubular outlet, and a core.
  • the core fluidically connects the tubular inlet to the tubular outlet via a plurality of tubes.
  • Each of the tubes has a helical shape and is circumferentially displaced from each of the others of the plurality of tubes.
  • the present disclosure is directed toward a heat exchanger that includes a first fluid manifold extending along a first fluid axis from a first fluid inlet to a first fluid outlet.
  • the first fluid manifold includes first fluid inlet and outlet headers, and a helical core section.
  • the inlet header is disposed to branch the first fluid inlet into a plurality of first fluid branches, and the outlet header is disposed to combine the plurality of first fluid branches into the first fluid outlet.
  • the helical core section fluidly connects the inlet header to the outlet header via a plurality of helical tubes, such that each helical tube corresponds to one of the plurality of first fluid branches.
  • FIG. 1 is schematized side view of a heat exchanger with a helical core.
  • FIG. 2 is an exaggerated perspective side view of the heat exchanger of FIG. 1 , in a compressed state.
  • a heat exchanger with a rotationally symmetric helical core is presented herein.
  • This helical core is made up of a plurality of structurally independent, circumferentially distributed and helical tubes. These tubes can be distributed in a cylindrically distributed spring arrangement.
  • the helical geometry of the core increases heat exchanger functional length and surface area as a function of the total axial length of the core, and provides structural compliance that allows the core to serve as a spring to relieve thermal and other stresses from the heat exchanger and adjacent (connecting) flow elements.
  • FIG. 1 is a schematized side view of heat exchanger 10 , which includes first fluid manifold 12 and second fluid guide 14 .
  • First fluid manifold 12 includes inlet header 16 , outlet header 18 , and core section 20 .
  • Inlet header 16 forks from inlet passage 22 into a plurality of inlet header branches 24
  • outlet header 18 recombines outlet header branches 26 into outlet passage 28 .
  • Core 20 is formed of a plurality of structurally independent helical tubes 30 that each extend from a separate inlet header branch 24 to a separate outlet header branch 26 .
  • hot fluid flow F 1 is provided to inlet header 16 , flows through core 20 , and exits through outlet header 18 . Thermal energy is transferred from hot fluid flow F 1 to cooling fluid flow F 2 as hot fluid flow F 1 passes through core 20 .
  • cooling fluid flow F 2 is not limited to the embodiments shown.
  • present disclosure refers to some flow as “cold” and other as “hot,” the present geometry can more generally be applied to any two fluid flows in a heat exchange relationship, e.g. wherein F 1 and F 2 are exchanged i.e. as cold and hot flows, respectively.
  • heat exchanger 10 is oriented substantially symmetrically along a fluid axis A, which connects extends from inlet passage 22 to outlet passage 28 .
  • axis A is a straight line defining a primary flow direction of hot fluid flow F 1 through first fluid manifold 12 .
  • heat exchanger 10 can extend along a contoured (non-straight) axis, e.g. due to space constraints.
  • Headers 16 , 18 distribute and receive fluid, respectively, substantially evenly across core 20 .
  • inlet header 16 splits into inlet header branches 24
  • outlet header 18 recombines from header branches 26 .
  • header 16 is a successively fractally branching manifold with multiple stages of branches, each narrowing in cross-sectional flow area with respect to the previous stage of less numerous branches, finally terminating in the full count of outlet header branches 22 as the narrowest and most axially distant from inlet passage 22 . More specifically, the present figures illustrate each stage of header 16 branching rotationally symmetrically about axis A into an even number of tubes evenly circumferentially distributed across a common plane transverse to axis A.
  • header 16 can be of any shape capable of distributing fluid from a single source at inlet passage 22 across the multitude of separate helical tubes 30 of core 20 .
  • the illustrated embodiment advantageously reduces pressure drop and provides additional mechanical compliance along axis A, within header 16 .
  • header 18 substantially mirrors header 16 , across core 20 .
  • headers 16 , 18 and core 20 are all formed monolithically.
  • all components of heat exchanger first fluid manifold 12 can be formed partially or entirely by additive manufacturing.
  • metal components e.g., Inconel, aluminum, titanium, etc.
  • exemplary additive manufacturing processes include but are not limited to powder bed fusion techniques such as direct metal laser sintering (DMLS), laser net shape manufacturing (LNSM), electron beam manufacturing (EBM).
  • DMLS direct metal laser sintering
  • LNSM laser net shape manufacturing
  • EBM electron beam manufacturing
  • stereolithography SLA
  • Additive manufacturing is particularly useful in obtaining unique geometries (e.g., varied core tube radii, arcuate core tubes, branched inlet and outlet headers) and for reducing the need for welds or other attachments (e.g., between headers 16 , 18 and core 20 ).
  • other suitable manufacturing process can be used.
  • header and core elements can in some embodiments be fabricated separately and joined via later manufacturing steps.
  • Second fluid guide 14 is illustrated schematically in FIG. 1 .
  • Second fluid guide 14 can be included in some embodiments to constrain cooling fluid flow F 2 .
  • Second fluid guide 14 is illustrated as a baffle surrounding mechanically unconnected to first fluid manifold 12 .
  • second fluid guide 14 can have additional sub-layers or separations to further channel cooling fluid flow F 2 through and across first fluid manifold 12 .
  • second fluid guide 14 can be omitted altogether, and first fluid manifold 12 directly exposed to an unconstrained environment of cooling fluid flow F 2 .
  • Second fluid guide 14 need not closely match the geometry of first fluid manifold 12 , but can in some embodiments parallel at least some aspects of the geometry of first fluid manifold, e.g.
  • second fluid guide 14 channels cooling fluid flow F 2 in a direction substantially antiparallel (i.e. parallel to but opposite) hot fluid flow F 1 .
  • second fluid guide 14 can instead direct cooling fluid flow F 2 in a direction transverse to F 1 , e.g. in a cross-flow direction.
  • Core section is formed by a plurality of separate, structurally independent helical tubes 30 .
  • Each helical tube 30 has a helical or spring-like geometry, extending axially and turning in common about fluid axis A.
  • Helical tubes 30 are distributed circumferentially about axis A, such that each helical tube 30 is substantially identical to all other tubes 30 , but shifted circumferentially relative to adjacent tubes. All tubes 30 are depicted as cross-sectionally distributed in a circular array across a plane orthogonal to fluid axis A. More generally, tubes 30 can be distributed in any array with rotational symmetry about fluid axis A, e.g.
  • Circular symmetry in the distribution of tubes 30 permits all tubes 30 to have identical geometry, with correspondingly identical and therefore uniform fluid flow and heat transfer characteristics. Asymmetric arrangements of tubes 30 , however, may be advantageous in tight space constraints, or where cooling fluid flow F 2 is non-uniform.
  • the spacing between adjacent helical tubes 30 is primarily circumferential, which provides a substantially uniform gap spacing between all adjacent tubes 30 , so as to promote even airflow F 2 therebetween. All helical tubes 30 can have a substantially identical and uniform inner diameter with a circular cross-section, resulting in equal cross-sectional areas. In the illustrated embodiment, the spacing between adjacent helical tubes 30 is greater than this inner diameter.
  • the rotational symmetry of helical tubes 30 within core 20 permits flow paths within headers 16 , 18 to be substantially equal in length, for greater uniformity in the distribution of fluid flow F 1 across tubes 30 relative to geometries with no such symmetry, or other symmetry types.
  • helical tubes 30 of core 20 serves several functions.
  • helical tubes 30 can be capable of compliantly deforming along axis A so as to accommodate thermal growth of headers 16 , 18 , and/or translation of headers 16 , 18 due to thermal growth of adjacent (upstream or downstream) components.
  • This mechanical compliance provided by core 20 allows heat exchanger to better distribute and weather thermal and other mechanical stresses.
  • FIG. 2 is an exaggerated (not to scale) perspective side view of heat exchanger 10 illustrating a compressed state of first fluid manifold 12 .
  • FIG. 2 illustrates the performance of core section 20 under such compression.
  • helical core 20 is significantly less compliant laterally, i.e. in dimensions transverse to fluid axis A.
  • This increased lateral stiffness provides first fluid manifold 12 with resonant frequencies of oscillation transverse to the first fluid flow that are greater than the range of operating frequencies of a surrounding engine or other components for at least its three highest amplitude natural frequencies, for example, so as to avoid excitation within the expected environment of heat exchanger 10 .
  • the generally circular cross-section of each tube 30 contributes to this increased lateral stiffness.
  • the helical geometry of tubes 30 also provides greater fluid flow length within each tube 30 , and correspondingly greater surface area exposed to cooling fluid flow F 2 .
  • the overall passage length of each tube 30 can, for example, be double the axial length of core 30 , or more.
  • Helical tubes 30 can introduce additional turbulence to fluid flows F 1 , F 2 , for additional heat transfer.
  • core 20 provides heat exchanger 10 with improved axial compliance to handle thermal stresses, increased lateral stiffness to avoid potentially harmful resonance conditions, and increased surface area exposed to cooling fluid flow F 2 for greater heat exchange, all with only modest pressure losses from inlet passage 22 to outlet passage 28 . Furthermore, the geometry of core 20 is symmetrical along two axes (axial and radial), and can consequently improve the uniformity of stress distribution across first fluid manifold 12 .
  • a heat exchanger comprising: a tubular inlet; a tubular outlet; and a core fluidically connecting the tubular inlet to the tubular outlet via a plurality of tubes each having a helical shape and circumferentially displaced from each of the others of the plurality of tubes.
  • a heat exchanger comprising: a fluid manifold extending along a first fluid axis from a first fluid inlet to a first fluid outlet, the first fluid manifold comprising: an inlet header disposed to fork the first fluid inlet into a plurality of first fluid branches distributed circumferentially about the first fluid axis; an outlet header disposed to combine the plurality of first fluid branches into the first fluid outlet; and a helical core section fluidly connecting the inlet header to the outlet header via a plurality of cylindrically arranged helical tubes, each helical tube corresponding to one of the plurality of first fluid branches.
  • the heat exchanger of the preceding paragraph can optionally include, additionally and/or alternatively, any one or more of the following features, configurations and/or additional components:
  • each of the plurality of helical tubes is structurally independent from all others of the plurality of helical tubes, such that the plurality of helical tubes are mechanically connected to each other only at the inlet header and the outlet header.
  • each of the plurality of helical tubes extends axially along and circumferentially about the first fluid axis.
  • a further embodiment of the foregoing heat exchanger wherein the first fluid axis extends linearly from the first fluid inlet passage to the first fluid outlet passage, and wherein the first fluid inlet and the first fluid outlet are themselves oriented along the first fluid axis.
  • each of the plurality of helical tubes is mechanically separated from adjacent of the plurality of helical tubes by a circumferential and axial gap.
  • a further embodiment of the foregoing heat exchanger wherein a structural rigidity of the first fluid manifold along the first fluid axis is less than along any radial dimension with respect to the first fluid axis.
  • a further embodiment of the foregoing heat exchanger wherein the first fluid manifold is situated in an environment with a known range of operating frequencies, and wherein the first fluid manifold has at least a highest amplitude natural resonance frequency of oscillation transverse to the first fluid axis that is greater than the known range of operating frequencies.
  • each of plurality of helical tubes has a total passage length at least double its extent along the first fluid axis.
  • a further embodiment of the foregoing heat exchanger wherein the helical core section forms a spring shape extending between the inlet header and the outlet header, wherein the spring shape is principally compliant along the first fluid axis.
  • a further embodiment of the foregoing heat exchanger wherein the helical core section is capable of compliantly deforming to accommodate axial growth of the inlet header and outlet header.
  • a further embodiment of the foregoing heat exchanger further comprising a second fluid flow structure disposed to direct a second fluid to impinge on the first fluid manifold, wherein the second fluid flow structure is configured to direct the second fluid generally along a direction from the first fluid outlet to the first fluid inlet.
  • inlet header branches the first fluid inlet passage into a first number N of first fluid branches
  • the plurality of helical tubes comprises N helical tubes even distributed circumferentially to form a cylindrical arrangement with a circumferential angular separation of 360°/N.
  • a further embodiment of the foregoing heat exchanger wherein the entirety of the first fluid manifold is formed monolithically as a single structure.
  • any relative terms or terms of degree used herein such as “substantially”, “essentially”, “generally”, “approximately” and the like, should be interpreted in accordance with and subject to any applicable definitions or limits expressly stated herein. In all instances, any relative terms or terms of degree used herein should be interpreted to broadly encompass any relevant disclosed embodiments as well as such ranges or variations as would be understood by a person of ordinary skill in the art in view of the entirety of the present disclosure, such as to encompass ordinary manufacturing tolerance variations, incidental alignment variations, alignment or shape variations induced by thermal, rotational or vibrational operational conditions, and the like.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Manufacturing & Machinery (AREA)
  • Materials Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US16/711,126 2019-03-08 2019-12-11 Cyllindrical helical core geometry for heat exchanger Abandoned US20200284519A1 (en)

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Application Number Priority Date Filing Date Title
US16/711,126 US20200284519A1 (en) 2019-03-08 2019-12-11 Cyllindrical helical core geometry for heat exchanger

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US201962815847P 2019-03-08 2019-03-08
US16/711,126 US20200284519A1 (en) 2019-03-08 2019-12-11 Cyllindrical helical core geometry for heat exchanger

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11209222B1 (en) * 2020-08-20 2021-12-28 Hamilton Sundstrand Corporation Spiral heat exchanger header
US11268770B2 (en) 2019-09-06 2022-03-08 Hamilton Sunstrand Corporation Heat exchanger with radially converging manifold

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102431918B1 (ko) * 2017-04-21 2022-08-11 커먼웰쓰 사이언티픽 앤드 인더스트리얼 리서치 오가니제이션 유동 분배 시스템

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4736533B2 (ja) * 2005-05-18 2011-07-27 パナソニック株式会社 熱交換器
WO2011115883A2 (en) * 2010-03-15 2011-09-22 The Trustees Of Dartmouth College Geometry of heat exchanger with high efficiency
DE102017203058A1 (de) * 2017-02-24 2018-08-30 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Wärmeübertrager und Reaktor
US10782071B2 (en) * 2017-03-28 2020-09-22 General Electric Company Tubular array heat exchanger
US10670349B2 (en) * 2017-07-18 2020-06-02 General Electric Company Additively manufactured heat exchanger

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11268770B2 (en) 2019-09-06 2022-03-08 Hamilton Sunstrand Corporation Heat exchanger with radially converging manifold
US12130090B2 (en) 2019-09-06 2024-10-29 Hamilton Sundstrand Corporation Heat exchanger with radially converging manifold
US11209222B1 (en) * 2020-08-20 2021-12-28 Hamilton Sundstrand Corporation Spiral heat exchanger header

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