EP2966391A1 - Wärmetauscher - Google Patents

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Publication number
EP2966391A1
EP2966391A1 EP14176288.0A EP14176288A EP2966391A1 EP 2966391 A1 EP2966391 A1 EP 2966391A1 EP 14176288 A EP14176288 A EP 14176288A EP 2966391 A1 EP2966391 A1 EP 2966391A1
Authority
EP
European Patent Office
Prior art keywords
turbulators
tubes
heat exchanger
rows
container
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
EP14176288.0A
Other languages
English (en)
French (fr)
Other versions
EP2966391B1 (de
Inventor
Fadil AYAD
Thierry Berger
Philippe Biver
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.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Priority to EP14176288.0A priority Critical patent/EP2966391B1/de
Priority to PCT/EP2015/065157 priority patent/WO2016005275A1/en
Publication of EP2966391A1 publication Critical patent/EP2966391A1/de
Application granted granted Critical
Publication of EP2966391B1 publication Critical patent/EP2966391B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F28D7/1692—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 with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core

Definitions

  • the present invention relates to heat exchanger for automotive applications.
  • a heat exchanger here a gas cooler, of the prior art comprises, enclosed in a container, a gas circuit and a coolant circuit arranged to thermally cooperate so that, gas flowing in longitudinal flat tubes of the gas circuit cools down while coolant circulating between the tubes heats-up.
  • the longitudinal flat tubes are stacked in a rectangular array arrangement of four non-contacting columns and about sixteen non-contacting rows.
  • turbulators are arranged between the tubes, said turbulators aiming at disturbing the coolant flow forcing it to oscillate in a longitudinal direction.
  • turbulators another more proper designation is offset strip fins.
  • the longitudinal flow direction of the coolant is also called the "hard way” while the transversal direction is the “easy way” as the obstacles are not as present as in the hard way.
  • First turbulators are arranged in the inter-rows space, horizontal space as per the orientation of the figure, in between each two adjacent tubes of a column. Said first turbulators aim at disturbing the coolant flow.
  • Second turbulators are arranged in the inter-columns space, vertical space as per the orientation of the figure, in between each two adjacent tubes of a row. Said second turbulators aim at preventing the coolant flow to shortcut said oscillating longitudinal path by "dropping" into said vertical space or, simply to prevent said coolant flow to deviate and change inter-rows in the inter-columns space.
  • the setting up of the first and second turbulators is delicate as the operators have to vertically stack columns of sandwiches of tubes and first turbulators then, to horizontally stack said sandwiches of columns and second turbulators.
  • aheat exchanger comprising a gas circuit and a coolant circuit enclosed in a container so that, in use, pressurized gas flowing in tubes and liquid coolant flowing between said tubes are in thermal exchange.
  • the heat exchanger further comprises turbulators, arranged in the coolant circuit, between the tubes, for generating, in use, turbulences of the coolant flow improving the thermal efficiency of the exchanger.
  • the turbulators are advantageously integrally formed in a turbulators plate extending across a plurality of tubes.
  • the turbulators plate integrally comprise first and second sections of turbulators, each comprising periodic pattern corrugations with spatial period along a longitudinal axis and normal peak-to-peak amplitude along a normal axis, perpendicular to said longitudinal axis.
  • the corrugations of the first section have smaller peak-to-peak amplitude than the corrugations of the second sections.
  • the tubes have a flat cross section and are arranged in a stack of parallel rows, one turbulators plate being arranged in the inter-rows space between adjacent rows of tubes.
  • each tube extends along the longitudinal axis from one longitudinal end of the container to the opposite longitudinal end and, the rows of tubes are arranged on a transverse direction from one lateral end of the container to the opposite lateral end of the container.
  • the turbulators plate extends across the entire area of the inter-rows space, in the longitudinal direction from said one longitudinal end of the container to said opposite longitudinal end and, in the transverse direction from said one lateral end of the container to said opposite lateral end of the container.
  • the arrangement of tubes is a two dimensional rectangular array comprising a plurality of rows and a plurality of columns.
  • the heat exchanger comprises at least four columns and at least ten rows.
  • the columns are non-contacting reserving inter-columns space and wherein the turbulators plates comprise integrally formed first corrugated sections arranged in the inter-rows space and second corrugated sections arranged in the inter-columns spaces.
  • the turbulators plates are arranged in neighbour inter-row spaces and cooperate with each other so that forming a continuous intermediate surface in the inter-columns space between adjacent tubes of the same row. The surface prevent the coolant to flow in the inter-column spaces.
  • the spatial period pattern of said corrugation is substantially a square wave alternating flat heads portions with flat feet portions.
  • the first section and the second section are arranged so that the second section extends above the first section by half the tube thickness t and extends below the first section by half the tube thickness.
  • the closed container within which are enclosed gas and coolant circuits is provided with a gas inlet and a gas outlet and, with a coolant inlet and a coolant outlet.
  • the gas in the gas circuit is pressurized carbon dioxide.
  • the invention further extends to a method to manufacture a heat exchanger, the method comprising the following steps:
  • the method further comprises the steps:
  • a heat exchanger here a liquid cooled gas cooler 10
  • the gas cooler 10 comprises a parallelepiped rectangle container 12 enclosing a gas circuit 14, for a gas to flow in two longitudinal ways L and, a coolant circuit 16 for coolant fluid to flow in oscillating about the longitudinal direction L.
  • the gas enters the container and flows in the longitudinal direction and, the coolant enters the container 12 and also flows along the longitudinal direction indicated by the large arrow FC.
  • This longitudinal flow direction of the coolant is known to be the "hard way” as, the path followed by the coolant is more tortuous and therefore the speed of the flow is reduced.
  • the coolant flows along the transversal "easy way", where its flow speed is superior.
  • the coolant flows only one time in the longitudinal direction before exiting the cooler 10.
  • the example of figure 1 is non-limiting as many other arrangements are known, especially gas cooler having another number of tubes arranged in different setting of rows and columns with flow in more than one direction.
  • the gas considered is carbon dioxide CO 2 , also referenced R744 in the standard list of refrigerating fluids and, the coolant is typically a glycol-type fluid.
  • the gas circuit 14 comprises flat tubes 18 extending along the longitudinal axis L and, in the transverse plan TN perpendicular to said longitudinal axis L, the tubes 18 are stacked in a two dimensional rectangular array, as sketched in figure 6 , comprising horizontal rows R and vertical columns C.
  • a two dimensional rectangular array as sketched in figure 6 , comprising horizontal rows R and vertical columns C.
  • horizontal spaces identified as inter-rows spaces IR are preserved between adjacent rows R
  • vertical spaces identified as inter-columns spaces IC are preserved between adjacent columns C.
  • the cross section, observed in the transverse plan TN of the flat tubes 18 have two opposite long sides 20 distant from each other by tube thickness t18, the long sides 20 extending along the transverse axis T and, said long sides 20 being connected at their extremities by two short sides 22, distant from each other by tube width w18.
  • the short sides 22 can be straight, forming a rectangle cross section, or curved such as in an oblong cross section.
  • the tubes 18 are sealingly and fluidly connected to manifolds 24 comprising the stack of a header plate, a distributor plate and of a closing plate, the latter also being a side plate of the container 12.
  • manifolds 24 comprising the stack of a header plate, a distributor plate and of a closing plate, the latter also being a side plate of the container 12.
  • one of the closing plates is provided with inlet 32 and outlet 34 pipes that are integrally formed in said closing plate.
  • the coolant flows in between the tubes 18 and, in each inter-rows space IR a large rectangular turbulators plate 36 is arranged.
  • the turbulators are so designated while more formal names are offset, or non-offset, strip fins.
  • Said plate 36 extends across the entire inter-row IR area, longitudinally from one header plate to the opposite header plate and, transversally across all columns C of tubes from one lateral side of the container 12 to the opposite lateral side.
  • the turbulators plate is now described in reference to figures 2 and 3 .
  • the turbulators plate 36 is a one piece integral plate that comprises longitudinal sections of first turbulators 38 alternating with longitudinal sections of second turbulators 40.
  • the first turbulators 38 comprise several corrugated strips, each having periodical square-shape pattern with spatial period P38 along the longitudinal axis L and, peak-to-peak amplitude A38 along the normal axis N. Said strips are next to each other, the patterns being longitudinally shifted so that globally, the direct longitudinal direction is obstructed, as better visible on figure 4 . This better explains the designation of "hard way" for the current flow along said direction.
  • the turbulators reserve transverse passages, figure 5 , forcing the coolant to follow a direction that is globally along said longitudinal axis L but oscillates about the axis L. This oscillated path creates turbulences that improve the thermal exchange compared to a straight laminar flow. Furthermore, said first sections of first turbulators 38 have a transverse width equal to the width w18 of a tube 18.
  • the sections of second turbulators 40 are narrower as they aim to be arranged in the inter-columns space IC in order to prevent the coolant from deviating in said inter-columns space IC and change inter-rows IR. Such a flow deviation would shortcut the coolant path and would diminish the thermal performance.
  • the second turbulators 40 are also made of a corrugated metal strip that has periodic square-pattern longitudinally L extending. Said square pattern of the second turbulators 40 has a spatial period P40 alternating heads 42 and feet portions 44 and, it also has normal peak-to-peak amplitude A40 with vertical, or normal, legs 46.
  • the first turbulators 38 have heads 42 and feet 44 portions in contact with the flat tubes 18, so the first turbulators have, because of heat transfer performance, a peak-to-peak amplitude A18 equal to the inter-rows normal distance dIR.
  • the inter-columns space IC is occupied by the second turbulators 40 with head portions 42 normally aligned N and, feet portions 44 also normally aligned N.
  • the second turbulators 40 cooperate and, in the inter-columns IC space an intermediate plan 48 is created alternating heads portion 42 of the turbulators 40 that is below on figure 5 and feet portions 44 of the turbulators 40 that is above in the stack.
  • the peak-to-peak amplitude A40 of the second turbulators 40 is greater than the peak-to-peak amplitude A38 of the first turbulators. It is such that said intermediate plan 48 is positioned on the median symmetrical plan MP of a row R.
  • said intermediate plan 48 is created between each and every adjacent tubes 18 of a row R.
  • the peak-to-peak amplitude A40 of the second turbulators 40 is chosen to normally N extend between two consecutive median plan MP so said amplitude A40 can be simply calculated as the sum of the first turbulators amplitude 38 plus the thickness t18 of the tubes.
  • a ⁇ 40 A ⁇ 38 + t ⁇ 18
  • the second turbulators 40 extend its amplitude A40 above and beyond the amplitude A38 of the first turbulators, by half the thickness, t18 / 2, of a flat tube 18.
  • An initial step 110 consists in providing individual components, such as flat tubes 18, turbulators plates 36, manifold 24 and container's side plates.
  • a subsequent step 120 consists in stacking a sandwich alternating a turbulators plate 36 and a row R of flat tubes 18.
  • this stacking step 120 would consist in arranging a turbulators plate 36 on a level surface and arranging a flat tube 18 in each of the first sections of first turbulators 38.
  • the turbulators plates 36 enable to pre-position and maintain in place the flat tubes 18. Said step 120 is repeated until the number of rows is made.
  • the integral turbulators plate 36 ease the stacking as each tube 18 is pre-positioned in a first section 38 and is maintained apart from its neighbor tube 18 by a second section 40.
  • the following steps consist in connecting the manifolds 24, enclosing the stack in the container plates and joining the assembly, for instance with a brazing operation.

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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)
EP14176288.0A 2014-07-09 2014-07-09 Wärmetauscher Not-in-force EP2966391B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP14176288.0A EP2966391B1 (de) 2014-07-09 2014-07-09 Wärmetauscher
PCT/EP2015/065157 WO2016005275A1 (en) 2014-07-09 2015-07-02 Heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14176288.0A EP2966391B1 (de) 2014-07-09 2014-07-09 Wärmetauscher

Publications (2)

Publication Number Publication Date
EP2966391A1 true EP2966391A1 (de) 2016-01-13
EP2966391B1 EP2966391B1 (de) 2017-03-08

Family

ID=51133940

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14176288.0A Not-in-force EP2966391B1 (de) 2014-07-09 2014-07-09 Wärmetauscher

Country Status (2)

Country Link
EP (1) EP2966391B1 (de)
WO (1) WO2016005275A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160313070A1 (en) * 2014-02-10 2016-10-27 Mitsubishi Heavy Industries Automotive Thermal Systems Co., Ltd. Heat-exchanger offset fin and refrigerant heat-exchanger utilizing same
WO2018029203A1 (de) * 2016-08-08 2018-02-15 Bundy Refrigeration International Holding B.V. Wärmetauscher mit mikrokanal-struktur oder flügelrohr-struktur
US10399683B2 (en) * 2016-02-16 2019-09-03 The Boeing Company Thermal management systems and methods
CN110546363A (zh) * 2017-02-28 2019-12-06 通用电气公司 包括限定内部流体通路的流湍流器的增材制造的热交换器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017219433B4 (de) * 2017-10-30 2022-08-11 Hanon Systems Wärmeübertrager für einen Verbrennungsmotor

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030010488A1 (en) * 2001-07-12 2003-01-16 Toshiharu Watanabe Cooling cycle
US20030106677A1 (en) * 2001-12-12 2003-06-12 Stephen Memory Split fin for a heat exchanger
DE102006046061A1 (de) * 2005-09-27 2007-04-19 Showa Denko Kabushiki Kaisha, Doing Business As Showa Denko K.K. Wärmetauscher
DE102012224353A1 (de) * 2012-12-21 2014-06-26 Behr Gmbh & Co. Kg Wärmeübertrager

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030010488A1 (en) * 2001-07-12 2003-01-16 Toshiharu Watanabe Cooling cycle
US20030106677A1 (en) * 2001-12-12 2003-06-12 Stephen Memory Split fin for a heat exchanger
DE102006046061A1 (de) * 2005-09-27 2007-04-19 Showa Denko Kabushiki Kaisha, Doing Business As Showa Denko K.K. Wärmetauscher
DE102012224353A1 (de) * 2012-12-21 2014-06-26 Behr Gmbh & Co. Kg Wärmeübertrager

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160313070A1 (en) * 2014-02-10 2016-10-27 Mitsubishi Heavy Industries Automotive Thermal Systems Co., Ltd. Heat-exchanger offset fin and refrigerant heat-exchanger utilizing same
US10399683B2 (en) * 2016-02-16 2019-09-03 The Boeing Company Thermal management systems and methods
WO2018029203A1 (de) * 2016-08-08 2018-02-15 Bundy Refrigeration International Holding B.V. Wärmetauscher mit mikrokanal-struktur oder flügelrohr-struktur
CN110546363A (zh) * 2017-02-28 2019-12-06 通用电气公司 包括限定内部流体通路的流湍流器的增材制造的热交换器
CN110546363B (zh) * 2017-02-28 2022-04-19 通用电气公司 包括限定内部流体通路的流湍流器的增材制造的热交换器

Also Published As

Publication number Publication date
WO2016005275A1 (en) 2016-01-14
EP2966391B1 (de) 2017-03-08

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