EP2909560A1 - Tube plat - Google Patents

Tube plat

Info

Publication number
EP2909560A1
EP2909560A1 EP13756175.9A EP13756175A EP2909560A1 EP 2909560 A1 EP2909560 A1 EP 2909560A1 EP 13756175 A EP13756175 A EP 13756175A EP 2909560 A1 EP2909560 A1 EP 2909560A1
Authority
EP
European Patent Office
Prior art keywords
flat
projections
walls
flat tube
interior
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
EP13756175.9A
Other languages
German (de)
English (en)
Other versions
EP2909560B1 (fr
Inventor
Steffen Brunner
Achim Herber
Jens Holdenried
Rainer STAUCH
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 Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP2909560A1 publication Critical patent/EP2909560A1/fr
Application granted granted Critical
Publication of EP2909560B1 publication Critical patent/EP2909560B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • 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
    • 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
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in 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
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples

Definitions

  • the invention relates to a flat tube with two oppositely disposed substantially parallel first walls and with two connecting the two flat first walls arcuate second walls, with an interior for the flow of a medium, wherein in at least one of the flat first walls projecting into the interior Projections are provided.
  • the invention also relates to a heat exchanger with such flat tubes.
  • flat tubes have been known as so-called rectangular tubes, which have two flat, broad side walls, which are connected by flat side walls. The corners between the flat wide and the flat side walls are provided with a small radius.
  • These flat tubes are essentially rectangular and are used for various types of heat exchanger.
  • these rectangular tubes are provided with projections projecting into the interior in order to improve the heat transfer between the flowing exhaust gas and the wall.
  • the projections are also referred to as winglets.
  • Outwardly projecting projections are also used as spacers between adjacent flat tubes, see also DE 10 2004 045 923 A1.
  • flat round flat tubes which have two flat wide side walls which are connected by arcuate side walls. These flat tubes are formed substantially rectangular-like with bulged side walls and are also used for different heat exchanger types.
  • these flat-round flat tubes are provided with projections projecting into the interior in the flat, broad side walls, in order to improve the heat transfer between the exhaust gas flowing through and the wall. Since, however, in these flat tubes, the width of the flat side wall is reduced compared to the rectangular tubes, because the lateral arc requires more space than a rectangular tube, the flat side wall, the embossed projections are narrower and the projections can not protrude into the regions of the fillets , This causes a reduced heat transfer in the flat round flat tube compared to the rectangular tube. Comparative measurements show reductions of up to 10%.
  • the flat-round flat tubes have the advantage that they show a significantly higher service life in thermoelectric loads than comparable rectangular tubes, since the fillets have a higher strength than the flat side walls of the rectangular tubes.
  • An embodiment of the invention relates to a flat tube with two oppositely disposed substantially parallel first walls and with two connecting the two flat first walls arcuate second walls, with an interior for flowing through an edum, wherein in at least one of the flat first walls are provided in the interior protruding projections, wherein in the arcuate second walls in the interior protruding projections are provided.
  • both opposing flat first walls each have projections projecting into the interior space. This leads to an increased power density.
  • both opposing arcuate second walls have protrusions protruding into the interior space.
  • the power density is increased because projecting projections are now provided on both end-side fillets.
  • at least one, preferably both, of the two opposite flat first walls have outwardly directed projections.
  • nubs are created as spacers between adjacent flat tubes, so that the distance of the tubes is defined and the flat tubes can touch only in small areas.
  • the inwardly directed projections of the flat first walls are arranged at a first repetition rate along the longitudinal axis of the flat tube. This results in a simpler production because the projections can be embossed periodically by means of embossing rollers or correspondingly repeating embossing tools.
  • the inwardly directed projections of the arcuate second walls are arranged at a second repetition rate along the longitudinal axis of the flat tube.
  • the projections can also be generated periodically by means of simplified tool design.
  • a repetition rate is an integer multiple, including 1, the other repetition rate. This limits the overall period length, which in turn facilitates a length variation of the tubes, and reduces the expense of periodically repeating tools.
  • the second repetition rate is twice as high as the first repetition rate.
  • the same power densities could be achieved with the flat-round flat tube, with the same pressure drop, as with a comparable rectangular tube.
  • the protruding projections of the flat first walls are arranged in an X-shaped and / or O-shaped manner. As a result, an optimized flow can be achieved. It is particularly advantageous if the outwardly projecting projections of the flat walls are arranged between the o-shaped protrusions of the first wall which project into the interior space.
  • the protrusions of opposing first walls projecting into the interior space are arranged complementary to one another so that an x-shaped arrangement in a first wall lies opposite an o-shaped arrangement opposite an opposite first wall.
  • an improved formation of turbulence is achieved.
  • the projections provided in the arcuate second walls and projecting into the interior space have an oval cross-section.
  • a projection in the arcuate second wall is arranged substantially at the level of the center of a projection in the flat first wall.
  • a favorable pipe design is created because the pipe constrictions are not arranged by the projections at the same height, which limits the pressure drop increase.
  • at least one end region or preferably both end regions of the roofing tube is or are formed without projections. This improves the boiling prevention in the tube of the heat exchanger.
  • the end regions have a length of about 5 mm to 50 mm, these end regions for the various projections can be different lengths. Preferably, 15 mm without any kind of projections and another 30mm without protrusions are performed to the outside.
  • At least one end region or preferably both end regions of the flat tube is or are formed without projections. This is particularly advantageous because Wtngtets, knobs and dents do not start on the same longitudinal coordinate of the pipe and / or must end.
  • the object of the present invention with respect to the heat exchanger is achieved by a heat exchanger with the features of claim 16.
  • FIG. 1 a shows a schematic view of a flat tube in a view from above
  • FIG. 1 b shows a schematic view of a flat tube in a view from the side
  • 1 c is a schematic view of a flat tube in a view from below
  • Fig.ld a schematic view of a flat tube in a front view
  • Fig.l e is a schematic view of a flat tube in a perspective view
  • 2b shows a schematic view of a flat tube in a front view
  • 2 c is a schematic view of a flat tube in a perspective view
  • 3a a schematic view of a section of a flat tube in a view from above
  • 3b shows a schematic view of a section of a flat tube in a view from below
  • 3 c is a schematic view of a projection in an arcuate wall
  • Figures 1 a to 1 e show an embodiment of a flat round flat tube
  • the two flat first walls 2, 3 are substantially flat and arranged parallel to each other.
  • the flat first walls 2, 3 are by means of arcuate second walls 4, 5 on the longitudinal side of the flat first walls
  • the arcuate second walls 4, 5 are semicircular or otherwise arcuate, formed.
  • the flat tube defines between the substantially flat first walls 2, 3 and the arcuate second walls 4, 5 an inner space 6 for the flow through the flat tube by means of a medium.
  • the medium is preferably exhaust gas or an exhaust gas-air mixture.
  • the flat tube is advantageously used as a tube of an exhaust gas cooler or intercooler.
  • projections 7 are impressed, which protrude into the interior 6 of the flat tube 1 in order to achieve there a turbulence of the flowing through the flat tube 1 medium.
  • the projections 7 are stamped as elongated projections 7 in the flat first wall 2, 3.
  • the projections 7 are x- shaped and o-shaped arranged in the opposite walls 2, 3 embossed »wherein the x-shaped indentations 8 alternate with the o-shaped indentations 9 viewed in the longitudinal direction of the flat tube 1.
  • An o-shaped arrangement of projections means that four of the projections are arranged diamond-shaped, so that they form a quasi ⁇ .
  • An x-shaped arrangement of projections means that four of the projections are arranged x- or star-shaped, so that they form an X virtually.
  • outwardly directed projections 10 are provided, which can serve as spacers of adjacent flat tubes 1, wherein the outwardly projecting projections 10 are arranged in the region of the o-shaped projections arranged.
  • the projections are arranged in the center of four o-shaped projections 7.
  • the arrangement of the projections 7 on a wall 2 in comparison to the arrangement of the projections 7 on the opposite wall 3 is offset from each other.
  • the arrangement of the outwardly projecting projections 10 is offset between opposite first walls 2, 3,
  • the periodicity of the projections 7 is plotted with the repeat length L, wherein the periodicity of the projections 1 1 is designated by the repeat length I.
  • the repeat length is the length after which the same pattern is repeated.
  • the repeat length l is in the figures 1 a to 1 e half the repetition length L, so that the recovery rate of the projections 1 1 is twice as high as the repetition rate of the projections 7.
  • the projections 11 are arranged opposite one another in both arcuate second walls 4, 5.
  • the projections 11 of an arcuate wall 4 could also be arranged offset relative to the projections 11 of the opposite wall 5.
  • FIGS. 2 a to 2 c show a further exemplary embodiment of a flat tube 21 according to the invention which, like the exemplary embodiment of FIGS. 1 a to 1 e, has substantially flat first walls 22, 23 which lie opposite one another and which are arranged parallel to one another.
  • the first walls 22, 23 are formed by second arcuate walls 24, 25 connected to each other.
  • projections, such as indentations, 27, 28 are provided in the flat first walls, which protrude from the first walls 22, 23.
  • the projections 27 protrude into the interior 26 and the projections 28 protrude outward.
  • projections 29 are also provided, which protrude into the interior 26.
  • the arrangement of the projections 27, 28 corresponds substantially to the arrangement of the projections 7, 10 of Figures 1a to 1 e, wherein the arrangement of the projections 29 substantially corresponds to the arrangement of the projections 1 1 of Figures 1 a to 1 e.
  • the difference between the embodiment of Figures 2a to 2c to the embodiment of Figures 1 a to 1 e is that the repeat length in the embodiment of Figures 2a to 2c the Wiederholpar L of the projections 27 corresponds.
  • Figures 3a and 3b show the arrangement of a projection 29 in relation to the arrangement of the projections 27. It can be seen that the center 30 of the projection 29 is approximately at the same height as the center 31 of a projection 27. The projection 29 is thus centered to a projection 27 which is connected to a group of Jumps 27 is arranged in an O-shape, wherein in the center of the O-shaped arrangement, a projection 28 is arranged.
  • FIG. 3 c shows by way of example the extension of a projection 29, wherein the extent transverse to the longitudinal direction of the flat tube, the embossing depth, is approximately 1.0 mm and the embossing radii and the outlet radii are each approximately 6.0 mm.
  • the embossing depth of the projections 29 can usefully be selected in the range between 0.5 mm and 1, 2 mm in order to protrude sufficiently deep into the interior relative to the arcuate second wall.
  • the impression is formed by a central recuperadtus with two marginal Auslaufradien.
  • the length, transverse to the embossing depth can advantageously amount to several times the embossing depth.
  • the projections 27 are arranged at an angle of approximately 22 ° to the longitudinal axis of the tube, wherein the projections 28 are round or oval, wherein, in the case of an oval shape, the longitudinal axis is arranged parallel to the longitudinal axis of the tube is.

Landscapes

  • 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)

Abstract

L'invention concerne un tube plat (1) comprenant deux premières parois (2, 3) pratiquement plates opposées et disposées parallèlement entre elles et deux deuxièmes parois (4, 5) en forme d'arc reliant les deux premières parois (2, 3) plates, un espace intérieur (6) pour la circulation d'un fluide, des saillies (7) s'avançant dans l'espace intérieur (6) étant prévues dans au moins une des premières parois (2, 3) plates et des saillies (11) s'avançant dans l'espace intérieur (6) étant prévues dans les deuxièmes parois (4, 5) en forme d'arc.
EP13756175.9A 2012-09-25 2013-09-03 Tube plat Active EP2909560B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012217333.1A DE102012217333A1 (de) 2012-09-25 2012-09-25 Flachrohr
PCT/EP2013/068192 WO2014048688A1 (fr) 2012-09-25 2013-09-03 Tube plat

Publications (2)

Publication Number Publication Date
EP2909560A1 true EP2909560A1 (fr) 2015-08-26
EP2909560B1 EP2909560B1 (fr) 2017-11-15

Family

ID=49085043

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13756175.9A Active EP2909560B1 (fr) 2012-09-25 2013-09-03 Tube plat

Country Status (4)

Country Link
US (1) US10520261B2 (fr)
EP (1) EP2909560B1 (fr)
DE (1) DE102012217333A1 (fr)
WO (1) WO2014048688A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3270085A1 (fr) * 2016-07-12 2018-01-17 Borgwarner Emissions Systems Spain, S.L.U. Échangeur thermique pour système egr
FR3069628A1 (fr) * 2017-07-31 2019-02-01 Valeo Systemes Thermiques Tube pour echangeur de chaleur avec dispositif de perturbation
WO2019025719A1 (fr) * 2017-07-31 2019-02-07 Valeo Systemes Thermiques Tube pour echangeur de chaleur avec dispositif de perturbation

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JP5850693B2 (ja) * 2011-10-05 2016-02-03 日野自動車株式会社 熱交換器用チューブ
DE102014108463B4 (de) * 2014-06-16 2020-03-05 Fischer Edelstahlrohre Gmbh Wärmeübertragerrohr, Wärmeübertrager und Verfahren zur Herstellung eines Wärmeübertragerrohrs
CN105300157A (zh) * 2014-07-08 2016-02-03 东风贝洱热系统有限公司 一种新型强化换热管
KR101922822B1 (ko) * 2014-08-12 2018-11-27 댄포스 마이크로 채널 히트 익스체인저 (지아싱) 컴퍼니 리미티드 열교환판 및 판형 열교환기
CN104567522A (zh) * 2014-10-29 2015-04-29 张博然 机翼式换热扁管
US20160123683A1 (en) * 2014-10-30 2016-05-05 Ford Global Technologies, Llc Inlet air turbulent grid mixer and dimpled surface resonant charge air cooler core
DE102015107927A1 (de) * 2015-05-20 2016-11-24 Volkswagen Aktiengesellschaft Flachrohrkühler und Verfahren zur Herstellung eines Flachrohrs
US20170010046A1 (en) * 2015-07-08 2017-01-12 Thermolift, Inc. Heat Exchanger
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DE102017222742A1 (de) * 2017-12-14 2019-06-19 Hanon Systems Rohr, insbesondere Flachrohr für einen Abgaskühler und Abgaskühler
DE102017223616A1 (de) 2017-12-21 2019-06-27 Mahle International Gmbh Flachrohr für einen Abgaskühler
US11391523B2 (en) * 2018-03-23 2022-07-19 Raytheon Technologies Corporation Asymmetric application of cooling features for a cast plate heat exchanger
CN110887396B (zh) * 2018-09-10 2021-03-05 浙江盾安热工科技有限公司 换热器扁管及具有其的换热器
CN111397426A (zh) * 2020-03-16 2020-07-10 南京理工大学 一种减弱管道截面热分层的强化传热装置
FR3129716B1 (fr) * 2021-11-30 2023-12-22 Valeo Systemes Thermiques Eléments de perturbation avancés pour l’amélioration de la performance des tubes

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Publication number Priority date Publication date Assignee Title
EP3270085A1 (fr) * 2016-07-12 2018-01-17 Borgwarner Emissions Systems Spain, S.L.U. Échangeur thermique pour système egr
FR3069628A1 (fr) * 2017-07-31 2019-02-01 Valeo Systemes Thermiques Tube pour echangeur de chaleur avec dispositif de perturbation
WO2019025719A1 (fr) * 2017-07-31 2019-02-07 Valeo Systemes Thermiques Tube pour echangeur de chaleur avec dispositif de perturbation

Also Published As

Publication number Publication date
DE102012217333A1 (de) 2014-03-27
US20150247680A1 (en) 2015-09-03
US10520261B2 (en) 2019-12-31
EP2909560B1 (fr) 2017-11-15
WO2014048688A1 (fr) 2014-04-03

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