EP3567332A1 - Wirbelndes zuführrohr für wärmetauscher - Google Patents

Wirbelndes zuführrohr für wärmetauscher Download PDF

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Publication number
EP3567332A1
EP3567332A1 EP19173305.4A EP19173305A EP3567332A1 EP 3567332 A1 EP3567332 A1 EP 3567332A1 EP 19173305 A EP19173305 A EP 19173305A EP 3567332 A1 EP3567332 A1 EP 3567332A1
Authority
EP
European Patent Office
Prior art keywords
inlet
walls
heat exchanger
flow
recited
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.)
Granted
Application number
EP19173305.4A
Other languages
English (en)
French (fr)
Other versions
EP3567332B8 (de
EP3567332B1 (de
Inventor
Corey D. Anderson
Jeremy STYBORSKI
Lauryn M. CURTIS
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
United Technologies Corp
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Filing date
Publication date
Application filed by United Technologies Corp filed Critical United Technologies Corp
Publication of EP3567332A1 publication Critical patent/EP3567332A1/de
Application granted granted Critical
Publication of EP3567332B1 publication Critical patent/EP3567332B1/de
Publication of EP3567332B8 publication Critical patent/EP3567332B8/de
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Anticipated expiration legal-status Critical

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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
    • F28F9/026—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
    • 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
    • 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
    • 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
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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 adjacent flow paths that transfer heat from a hot flow to a cooling flow.
  • the flow paths are defined by a combination of plates and fins that are arranged to transfer heat from one flow to another flow.
  • Thermal gradients present in the sheet material create stresses that can be very high in certain locations. Increasing temperatures and pressures can result in stresses on the structure that can exceed material and assembly capabilities.
  • Turbine engine manufactures utilize heat exchangers throughout the engine to cool and condition airflow for cooling and other operational needs. Improvements to turbine engines 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.
  • a heat exchanger assembly in a featured embodiment, includes an inlet manifold defining an expanding area in a direction of flow; and an inlet in flow communication with the inlet manifold, the inlet including a wall for inducing a rotational inertia to flow entering the inlet manifold.
  • the inlet comprises a constant cross-sectional area over an inlet length prior to the inlet manifold.
  • the inlet comprises a pipe and the wall comprises a plurality of walls spirally arranged within the inlet length.
  • the pipe is round and includes an inner surface and the plurality of walls are disposed transverse to the inner surface.
  • the plurality of walls include a height and the height is less than a width of the pipe.
  • the plurality of walls extend across a width of the pipe and define separate channels.
  • the plurality of walls are continuous for the entire inlet length.
  • the plurality of walls are intermittently arranged for at least a portion of the inlet length.
  • a density of walls is uniform for the entire inlet length.
  • a density of walls varies within the inlet length.
  • a distance between the plurality of walls in a direction parallel to a longitudinal axis and an angle of the walls relative to the longitudinal axis and a swirl induced into the inlet flow is determined by a combination of the distance between the plurality of walls and the angle.
  • At least one of the distance between the plurality of walls and angle of the plurality of walls varies over a length of the inlet.
  • a heat exchanger assembly including an inlet manifold defining an increasing flow area.
  • a plate fin heat exchanger plate includes a first end in flow communication with the inlet manifold and including a plurality of inlet openings arranged across an inlet width.
  • An inlet communicating flow to the inlet manifold includes a means for inducing a spiral flow for spreading flow through the inlet manifold across the inlet width.
  • the inlet includes a uniform cross-sectional flow area over an inlet length.
  • inlet comprises a pipe and the means for introducing a spiral inertial comprises a plurality of walls spirally arranged and extending from an interior surface of the pipe within the inlet length.
  • the plurality of walls include a height from the inner surface and the height that is less than a width of the pipe.
  • the plurality of walls extend define separate channels within the inlet.
  • a method of assembling a heat exchanger assembly includes forming an inlet manifold to include an expanding flow area, attaching the inlet manifold to a plate fin heat exchanger that includes a plurality of openings disposed across an inlet width. Forming an inlet to include a constant flow area and a spiral flow inducing means; and attaching the inlet to the inlet manifold for spreading flow entering the inlet manifold across inlet width.
  • the spiral flow inducing means comprises a plurality walls extending inward from an inner surface that are arranged in a spiral along an inlet length.
  • At least one of a distance between the plurality of walls in a direction common with a longitudinal axis of the inlet and an angle of the plurality of walls relative to the longitudinal axis is defined to induce a defined swirl component into the flow entering the inlet manifold.
  • an example heat exchanger 10 includes an inlet manifold 12 that feeds hot airflow 18 to a plate fin heat exchanger 14.
  • the plate fin heat exchanger 14 includes an inlet end 32 attached to the inlet manifold 12 and an outlet end 34 attached to the outlet manifold 16.
  • the hot flow 18 is communicated through an opening 30 of an inlet pipe 22 to the inlet manifold 12 and thereby to the plate fin heat exchanger 14.
  • a cooling airflow 20 flows over the plate fin heat exchanger 14 and accepts heat from the hot flow 18.
  • Outgoing hot flow 18 through the exhaust outlet manifold 16 is of a cooler temperature than the hot flow 18 into the inlet manifold 12.
  • the plate fin heat exchanger 14 includes a plurality of internal passages schematically shown at 26 and an outer surface including a plurality of fins 24. Each of the passages 26 is in communication with the inlet end 32 that includes a plurality of openings 36. The openings 36 are disposed across an inlet width 28 that is in communication with the inlet manifold 12.
  • a typical inlet manifold 112 receives flow from an inlet pipe 122.
  • the flow projects into the manifold 112 and does not expand uniformly toward outer areas schematically indicated at 125. Instead, the flow concentrates within a center region 116 of the manifold and the corresponding center passages 126 within a heat exchanger 114.
  • the non-uniform distribution of flow in to the heat exchanger 114 reduces heat transfer efficiency.
  • the disclosed example inlet manifold 12 includes a first area 40 near the inlet pipe 22 and a second area 42 near the inlet end 32.
  • the first area 40 is much smaller than the second area 42.
  • the inlet manifold 12 includes an expanding cross-sectional flow area in a direction towards the plate fin heat exchanger 14 inlet end 32.
  • the rapidly increasing flow area within the inlet manifold 12 can cause distribution problems of flow entering from the inlet pipe 22. Flow entering from the inlet pipe 22 will proceed towards the center most passages of the plate fin heat exchanger 14 potentially leaving gaps of lower flow to areas indicated schematically at 25 near the inlet end 32.
  • the example inlet pipe 22 includes a means for distributing flow entering the inlet manifold 12 across the entire width 28 of the inlet end 32.
  • the means for distributing flow includes a plurality of walls 38 on the inner surface of the inlet pipe 22 to induce a spiral flow to the incoming flow to uniformly distribute flow along the inlet width 28.
  • the example inlet pipe 22 includes an inlet length 44 with a substantially constant flow area.
  • the walls 38 are provided within the inlet length 44, but may also extend throughout the entire inlet pipe 22.
  • the walls 38 may also be provided only within the inlet length 44.
  • the inlet length 44 is a length that is predetermined to provide sufficient turns to induce the desired spiral component to incoming hot flow 18.
  • the walls 38 are twisted within the inlet pipe 22 to induce a spiral flow component inlet manifold 12.
  • the induced spiral flow components drive flow towards the extremes of the inlet width 28 schematically indicated at 25.
  • the mixing and distributions provided by the swirling flows provide a more uniform distribution of the hot flow 18 into the plate fin heat exchanger 14.
  • sections of the inlet pipe 22 are illustrated for the inlet length 44 and show the twist of one wall section 46 at different positions about the circumference of the inlet pipe 22.
  • the wall section 46 spirally winds along the inner surface of the inlet pipe 22.
  • Each of the walls 46 extends a height 54 from the internal surface 48.
  • the height 54 is much less than a width 52 of the inlet pipe 22.
  • the width 52 in the disclosed example inlet 22 is a diameter of the inlet 22.
  • the example inlet 22 is a circular pipe including a circular inner surface 48.
  • Each of the walls 46 extend the height 54 towards the center portion of the inlet 22.
  • each of the walls 46 are disposed transversally at an angle 50 normal to the inner surface 48. It should be appreciated that the walls 46 may be disposed at an angle other than normal to provide a desired flow component into the inlet manifold 12.
  • circumferential spacing between the walls 46 define channels 56 for the flow 18.
  • the spiral round channels 56 induce a spiral swirling component into the flow that carries forward through the inlet manifold 12.
  • the spiral component to the inlet hot flow 18 drives portions of the flow toward the sides of the inlet end 32 to more uniformly distribute flow into the heat exchanger plate 14.
  • an example inlet 22' includes the example walls 46 are spaced apart to define channels 58.
  • the walls 46 are spaced the distance 58 to provide a defined density along the inlet length 44.
  • the density of walls 46 within the inlet length 44 is provided to define a desired amount of swirl into the inlet flow.
  • FIG. 8 another example inlet 60 is disclosed includes spacing 64 that is greater than the spacing 58 described in the previous embodiment.
  • the increased spacing 64 illustrates a different density of walls 62 within the inlet 22 to enable tuning specific flow parameters designed to spread incoming flow across the passages 36.
  • FIG. 9 another example inlet 68 is disclosed and includes a plurality of walls 70 that are intermittent and includes spaces 72 therebetween.
  • the spaces 72 demonstrate that walls 70 need not be uniform or constant throughout the entire inlet length 44.
  • the inlet pipe 68 includes intermittent walls 70 that provide the desired inducement of swirl into the incoming flow.
  • density is also be changed by varying an angle 90 of the walls 92.
  • the angle 90 defines the length that an individual wall 92 needs to rotate 360 degrees about the interior wall of the inlet pipe.
  • the space 88 between the walls 92 is a function of the angle 90 and the number of walls 92 within a length 95 of the inlet cross section.
  • the changing angle 90 enables tailoring a swirl rate of airflow through the inlet.
  • the swirl rate is modified as function of the angle 90 and the number of walls 92 within the length 95 of the inlet. The steeper the angle 90, the more turns for the same length 95.
  • increasing or reducing the number of walls 92 also can be tailored to provide a desired swirl in the incoming flow.
  • An inlet 82 shown in Figure 10a includes walls 92 that are a distance 88a apart and disposed at an angle 90a relative to a longitudinal axis A.
  • the angle 90a and number of walls 92 for the length 95 defines a density that is tailored to induce a predefined swirl into the flow exiting the inlet 82.
  • the example angle in one disclosed embodiment, is less than 90 degrees and more than 45 degrees.
  • the distance 88a is a function of the angle 90a of the walls 92 in the defined length 95.
  • FIG. 10b Another inlet 84 shown in Figure 10b includes walls 92 that disposed at an angle 90b combined with a number of walls 92 that provides a spacing 88b that is less than the spacing 88a shown in Figure 10a .
  • the angle 90a remains the same, but increasing the number of walls 92 decrease in the spacing 88b to provide increased swirl for the same length 95.
  • a further inlet 86 shown in Figure 10c includes an angle 90b that is not as steep as the previous angle 90a.
  • the number of walls 92 is reduced and therefore the distance 88c is greater than either that shown in Figures 10a and 10b .
  • the different angle 90b with a reduced number of walls 92 provides a larger spacing 88c to induce the desired defined swirl in the inlet flow.
  • the swirl provided by the walls 92 of the inlet 86 can have any number of variation of the walls 92 and angles 90 to provide different spacings 88 to induce different swirl in flows exiting the inlet tube.
  • FIG. 11a, 11b, and 11c another example inlet 76 is disclosed and includes a plurality walls 78 defining a corresponding plurality of closed passages 80 that spirally wind along the inlet length 44.
  • the plurality of separate passages 80 induce swirl components into the incoming airflow to uniformly spread and distribute airflow along the inlet end 32 of the plate fin heat exchanger 14.
  • the disclosed inlet pipe induces flow characteristics that aid in more uniformly distributing the hot airflow throughout the passages of the heat exchanger.

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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)
EP19173305.4A 2018-05-08 2019-05-08 Wirbelndes zuführrohr für wärmetauscher Active EP3567332B8 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US15/973,709 US20190346216A1 (en) 2018-05-08 2018-05-08 Swirling feed tube for heat exchanger

Publications (3)

Publication Number Publication Date
EP3567332A1 true EP3567332A1 (de) 2019-11-13
EP3567332B1 EP3567332B1 (de) 2021-01-06
EP3567332B8 EP3567332B8 (de) 2021-03-31

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ID=66448474

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Application Number Title Priority Date Filing Date
EP19173305.4A Active EP3567332B8 (de) 2018-05-08 2019-05-08 Wirbelndes zuführrohr für wärmetauscher

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US (1) US20190346216A1 (de)
EP (1) EP3567332B8 (de)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005042315A1 (de) * 2005-09-06 2007-03-08 Behr Gmbh & Co. Kg Kühlmittelkühler, insbesondere für ein Kraftfahrzeug
EP2998684A1 (de) * 2014-09-22 2016-03-23 MAHLE International GmbH Vorrichtung zur zuführung eines kühlmittels zu einem wärmeübertrager, vorzugsweise für einen abgaskühler eines verbrennungsmotors eines kraftfahrzeuges

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2768814A (en) * 1950-10-27 1956-10-30 Frey Plate warmer exchanger
US3394736A (en) * 1966-02-21 1968-07-30 Acme Ind Inc Internal finned tube
US4174750A (en) * 1978-04-18 1979-11-20 Nichols Billy M Tube cleaner having anchored rotatable spiral member
US4305460A (en) * 1979-02-27 1981-12-15 General Atomic Company Heat transfer tube
US5110560A (en) * 1987-11-23 1992-05-05 United Technologies Corporation Convoluted diffuser
EP0586747A1 (de) * 1992-09-10 1994-03-16 The Procter & Gamble Company Wärmetauschersystem mit Turbulator für Dispersion von Teilchen in Flüssigkeit
CA2384375A1 (en) * 1999-09-10 2001-03-15 Martin R. Kasprzyk Insert for a radiant tube
US6382313B2 (en) * 2000-02-25 2002-05-07 Nippon Shokubai Co., Ltd. Heat exchanger for easily polymerizing substance-containing gas provided with gas distributing plate
EP1561795B1 (de) * 2002-11-15 2014-04-02 Kubota Corporation Crackrohr mit spiralfinne
EP1793164A1 (de) * 2005-12-05 2007-06-06 Siemens Aktiengesellschaft Dampferzeugerrohr, zugehöriges Herstellungsverfahren sowie Durchlaufdampferzeuger
JP2017125633A (ja) * 2016-01-12 2017-07-20 住友精密工業株式会社 熱交換器
EP3309494B1 (de) * 2016-10-13 2021-04-28 HS Marston Aerospace Limited Wärmetauscher

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005042315A1 (de) * 2005-09-06 2007-03-08 Behr Gmbh & Co. Kg Kühlmittelkühler, insbesondere für ein Kraftfahrzeug
EP2998684A1 (de) * 2014-09-22 2016-03-23 MAHLE International GmbH Vorrichtung zur zuführung eines kühlmittels zu einem wärmeübertrager, vorzugsweise für einen abgaskühler eines verbrennungsmotors eines kraftfahrzeuges

Also Published As

Publication number Publication date
US20190346216A1 (en) 2019-11-14
EP3567332B8 (de) 2021-03-31
EP3567332B1 (de) 2021-01-06

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