EP2384837A2 - Procédé de fabrication d'un tube d'échange thermique et échangeur thermique - Google Patents

Procédé de fabrication d'un tube d'échange thermique et échangeur thermique Download PDF

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Publication number
EP2384837A2
EP2384837A2 EP11163326A EP11163326A EP2384837A2 EP 2384837 A2 EP2384837 A2 EP 2384837A2 EP 11163326 A EP11163326 A EP 11163326A EP 11163326 A EP11163326 A EP 11163326A EP 2384837 A2 EP2384837 A2 EP 2384837A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
max
tube
section
exchanger tube
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
EP11163326A
Other languages
German (de)
English (en)
Other versions
EP2384837B1 (fr
EP2384837A3 (fr
Inventor
Ingo Toparkus
Rainer Vösgen
Nicole Rotzoll
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.)
Benteler Automobiltechnik GmbH
Original Assignee
Benteler Automobiltechnik 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 Benteler Automobiltechnik GmbH filed Critical Benteler Automobiltechnik GmbH
Publication of EP2384837A2 publication Critical patent/EP2384837A2/fr
Publication of EP2384837A3 publication Critical patent/EP2384837A3/fr
Application granted granted Critical
Publication of EP2384837B1 publication Critical patent/EP2384837B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/06—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of metal tubes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D15/00—Corrugating tubes
    • B21D15/12—Bending tubes into wave form
    • 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
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal 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
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • F28F21/083—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys from stainless steel
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49391—Tube making or reforming

Definitions

  • the present invention relates to a method for producing a heat exchanger tube having the features of patent claim 1 and an exhaust gas-carrying heat exchanger having the features of patent claim 10.
  • the heat exchangers In addition to the higher heat transfer performance requirements, the heat exchangers must be able to operate at increasingly higher pressures. In particular, in the heat exchangers, which flows through a gaseous fluid to be cooled, the demand for the pressure to be transmitted increases increasingly by ever higher engine charging levels. In addition, a low pressure loss within the heat exchanger is increasingly required.
  • the flow coefficients of the body are being optimized more and more, which adversely affects the cooling capacity of the heat exchanger with smaller cooling holes.
  • the total weight of the vehicle should drop, so that low fuel consumption and thus lower CO 2 emissions can be realized.
  • Object of the present invention is therefore to provide a cost-effective and efficient method for producing a heat exchanger tube and a heat exchanger with the heat exchanger tubes produced by the method available, which has a high cooling capacity, low flow resistance and compact space dimensions.
  • a tube with a circular cross section is formed into a tube with a non-circular cross section, preferably a rectangular cross section, and the tube with a non-circular cross section is corrugated in its longitudinal direction and / or transverse direction.
  • the inventive method for producing a heat exchanger tube has the particular advantage that a heat exchanger tube with compact space dimensions and high pressure tightness can be produced.
  • a substantially circular tube which may be formed, for example, by a roll-rolled longitudinally welded pipe, a tube with a non-circular cross section is produced by a forming process.
  • a non-circular cross-section may, for example, be an oval, an elliptical, preferably a rectangular cross-section and / or a hybrid form of the aforementioned cross-sectional shapes.
  • the thus produced substantially non-circular tube profile has an approximately equal pressure resistance compared to a round tube profile.
  • the originally circular tube is referred to as round tube profile
  • the heat exchanger tube is provided with a wave shape in the longitudinal and / or transverse direction.
  • the amplitude of the waveform may be formed by referring to the longitudinal direction as an X-axis in both the Y and Z-axis directions. It is also conceivable to make a combination of training in the Y and Z directions.
  • the waveform may also be formed in the transverse direction of the heat exchanger tube. This results, for example, in cross-section a tendency U-shaped or S-shaped configuration of previously converted to a non-circular cross-section tube.
  • the waveform is made with an amplitude corresponding to 0.2 to 1.2 times an outer diameter of the round tube profile.
  • an amplitude is produced which corresponds to 0.5 to 0.75 times the outside diameter of the round tube profile.
  • the amplitude corresponds to the height of the respective deflection of the waveform in the Y or Z-axis direction.
  • the heat exchanger tube is manufactured with a wave shape having a wavelength which corresponds to 1 to 7 times the outside diameter of the round tube profile.
  • the wavelength corresponds to 3 to 6 times the outer diameter of the round tube profile.
  • the heat exchanger tube is made of a stainless steel.
  • a stainless steel is to be understood in the context of the invention significantly a stainless steel.
  • an austenitic steel can be used in the invention. In particular, this results in the advantage that the high demands placed on the corrosion resistance of the steel material used in an application in an exhaust system of a vehicle are achieved.
  • chemically aggressive cooling media such as cooling water with cooling additive
  • the heat exchanger on the other hand, it is corrosive gases.
  • the heat exchanger is subject to strong thermal fluctuations.
  • the steel provides a particularly good thermal conductivity, which is transferred from one medium to the other by convection and heat conduction within the heat exchanger and thus ensures high efficiency of the heat exchanger.
  • a stainless steel By using a stainless steel, a high longevity of the heat exchanger is realized.
  • one of the following stainless steel alloys is expressed with the respective alloy constituents used in wt .-% for the production of a heat exchanger tube according to the invention.
  • Alloy Carbon (C): Max. 0.03 Silicon (Si): Max. 1.0 Manganese (Mn): Max. 2.0 Phosphorus (P): Max. 0,045 Sulfur (S): Max.
  • the subject portion of the invention is achieved with an exhaust gas-carrying heat exchanger, wherein the heat exchanger has a plurality of heat exchanger tubes produced by a method according to the invention, dissolved.
  • the exhaust gas-carrying heat exchanger produced in this way can cost-effective and production-safe a large contact surface between the create heat-absorbing fluid and the heat-emitting fluid.
  • the result is an increased heat output, which can be attributed to an extension of the flow path and turbulence within the flowing fluid or vortex formations. This happens depending on the arrangement of the exhaust gas-carrying heat exchanger on both sides of the fluid used, for example in DC, countercurrent or cross-flow direction.
  • the exhaust-gas-carrying heat exchanger has heat exchanger tubes which have a varying amplitude or even wavelength in the tube longitudinal direction.
  • the turbulences generated by the waveform can be varied in the flow channel to optimize resulting pressure losses or also contact areas in the form of laminar flow to be able to.
  • This also creates the advantage that at high turbulence, generated by strong flow channel ripple, the performance of the heat exchanger operates in an efficient range even with small temperature differences between the two fluids flowing through the heat exchanger.
  • the heat exchanger tubes may be designed to be helical in the dimensions of the longitudinal direction-related extent of the waveform in two dimensions, for example.
  • a double-helical design of the heat exchanger tubes is conceivable.
  • FIG. 1 shows a heat exchanger tube 1 according to the invention in a side view.
  • the heat exchanger tube 1 has a waveform in the longitudinal direction 2.
  • the waveform has, relative to the plane of the drawing, in the vertical direction, a height exhibition in the form of an amplitude 4 and in the horizontal direction, a wavelength 5.
  • the wavelength 5 is limited by the distance from wave trough WT to wave trough WT or wave mountain WB to Wellenberg WB.
  • FIG. 2 shows a perspective view of the heat exchanger tube 1.
  • the heat exchanger tube 1 is formed in cross-section substantially by a rectangular cross-section 6.
  • the rectangular cross-section 6 is flat in each case with reference to the image plane on its upper side 7 and its underside 8. In side regions 9, it has a curvature 10.
  • this curvature 10 can have an advantageous effect on the flow S and the resulting flow resistance.
  • the inner flow direction Si relative to the coordinate system, extends essentially in the X direction and the amplitude 4 is aligned in the Y direction for this purpose.
  • the width b of the heat exchanger tube according to the invention is preferably 0.5 to 12.0 mm.
  • FIG. 3 shows a heat exchanger 11 according to the invention in a side view.
  • the heat exchanger 11 consists of several combined heat exchanger tubes 1, which are coupled together at their ends 12 via tube sheets 13.
  • the coupling of the ends 12 of the heat exchanger tubes 1 with the tubesheets 13 can be effected by a positive connection, adhesion or even material connection in a respective end region of the heat exchanger tube 1.
  • the heat exchanger tubes 1 are arranged in total so that the troughs of adjacent heat exchanger tubes 1 lie in one plane. The tubes are therefore not offset from each other in the longitudinal direction. This results in a high packing density.
  • FIG. 4 shows a cross-sectional view of a circular tube 3.
  • the circular tube 3 has an outer diameter D in its initial state. It serves as a semi-finished product for the production of the heat exchanger tube 1 and is flattened and corrugated accordingly. With respect to the outer diameter D, the amplitude 4 and the wavelength 5 of the waveform are set.
  • FIG. 5 shows a side view of a heat exchanger tube 1 according to the invention, in which case the wavelength L (shown in the other figures as reference numeral 5), the height of the total pipe H. a radius of a wave trough R, a flow area G and a simple wave height A are shown.
  • L shown in the other figures as reference numeral 5
  • H / L G HA G / H R / H 0.1 to 0.3 -4 to 2 mm -1 to 1 1 to 5

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP11163326.9A 2010-05-03 2011-04-21 Procédé de fabrication d'un tube d'échange thermique Not-in-force EP2384837B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010019241A DE102010019241A1 (de) 2010-05-03 2010-05-03 Verfahren zur Herstellung eines Wärmetauscherrohres und Wärmetauscher

Publications (3)

Publication Number Publication Date
EP2384837A2 true EP2384837A2 (fr) 2011-11-09
EP2384837A3 EP2384837A3 (fr) 2012-04-04
EP2384837B1 EP2384837B1 (fr) 2013-11-06

Family

ID=44358416

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11163326.9A Not-in-force EP2384837B1 (fr) 2010-05-03 2011-04-21 Procédé de fabrication d'un tube d'échange thermique

Country Status (3)

Country Link
US (1) US20120111548A1 (fr)
EP (1) EP2384837B1 (fr)
DE (1) DE102010019241A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013131922A3 (fr) * 2012-03-06 2013-10-31 Babcock Borsig Steinmüller Gmbh Échangeur de chaleur résistant à la corrosion
CN104185315A (zh) * 2013-05-24 2014-12-03 陈树炼 波浪型电热构造及其制造方法
WO2015016726A1 (fr) 2013-08-02 2015-02-05 Aic S.A. Tuyau d'échangeur de chaleur à combustion
FR3026164A1 (fr) * 2014-09-24 2016-03-25 Valeo Systemes Thermiques Echangeur de chaleur pour vehicule automobile
FR3030029A1 (fr) * 2014-12-16 2016-06-17 Commissariat Energie Atomique Plaque d'echange thermique a microcanaux et echangeur thermique comportant au moins une telle plaque
WO2017007354A1 (fr) 2015-07-05 2017-01-12 Aic Spółka Akcyjna Tube de conduit d'air d'échangeur de chaleur évaporateur
WO2017007355A1 (fr) 2015-07-05 2017-01-12 Aic Społka Akcyjna Tube de fumée d'échangeur de chaleur à condensation
WO2018070889A1 (fr) 2016-10-13 2018-04-19 Aic Spółka Akcyjna Tube à flamme d'un échangeur de chaleur chauffé
CN109108129A (zh) * 2018-10-15 2019-01-01 西北工业大学 一种波纹管的管轴压成形方法

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CN103047882A (zh) * 2013-01-11 2013-04-17 哈尔滨工程大学 波浪管折流栅式方形换热器
CN103017570A (zh) * 2013-01-14 2013-04-03 哈尔滨工程大学 微波浪管与直管混合排列自支撑式换热器
US9724746B2 (en) * 2013-03-14 2017-08-08 Pratt & Whitney Canada Corp. Aerodynamically active stiffening feature for gas turbine recuperator
CN103307813B (zh) * 2013-07-05 2016-08-17 丹佛斯微通道换热器（嘉兴）有限公司 换热器及其成形方法
US9845729B2 (en) 2013-10-08 2017-12-19 Pratt & Whitney Canada Corp. Method of manufacturing recuperator air cells
CN106152853A (zh) * 2015-04-09 2016-11-23 丹佛斯微通道换热器（嘉兴）有限公司 波浪形扁管、扁管加工设备以及扁管形成方法
US11112183B2 (en) * 2016-01-14 2021-09-07 Hamilton Sundstrand Corporation Heat exchanger channels
US20190257592A1 (en) * 2018-02-20 2019-08-22 K&N Engineering, Inc. Modular intercooler block
US11098962B2 (en) * 2019-02-22 2021-08-24 Forum Us, Inc. Finless heat exchanger apparatus and methods

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013131922A3 (fr) * 2012-03-06 2013-10-31 Babcock Borsig Steinmüller Gmbh Échangeur de chaleur résistant à la corrosion
CN104185315A (zh) * 2013-05-24 2014-12-03 陈树炼 波浪型电热构造及其制造方法
WO2015016726A1 (fr) 2013-08-02 2015-02-05 Aic S.A. Tuyau d'échangeur de chaleur à combustion
FR3026164A1 (fr) * 2014-09-24 2016-03-25 Valeo Systemes Thermiques Echangeur de chaleur pour vehicule automobile
EP3001133A1 (fr) * 2014-09-24 2016-03-30 Valeo Systemes Thermiques Échangeur de chaleur pour véhicule automobile
FR3030029A1 (fr) * 2014-12-16 2016-06-17 Commissariat Energie Atomique Plaque d'echange thermique a microcanaux et echangeur thermique comportant au moins une telle plaque
WO2016097032A1 (fr) * 2014-12-16 2016-06-23 Commissariat à l'énergie atomique et aux énergies alternatives Plaque d'echange thermique a microcanaux et echangeur thermique comportant au moins une telle plaque
WO2017007354A1 (fr) 2015-07-05 2017-01-12 Aic Spółka Akcyjna Tube de conduit d'air d'échangeur de chaleur évaporateur
WO2017007355A1 (fr) 2015-07-05 2017-01-12 Aic Społka Akcyjna Tube de fumée d'échangeur de chaleur à condensation
WO2018070889A1 (fr) 2016-10-13 2018-04-19 Aic Spółka Akcyjna Tube à flamme d'un échangeur de chaleur chauffé
CN109108129A (zh) * 2018-10-15 2019-01-01 西北工业大学 一种波纹管的管轴压成形方法

Also Published As

Publication number Publication date
EP2384837B1 (fr) 2013-11-06
US20120111548A1 (en) 2012-05-10
DE102010019241A1 (de) 2011-11-03
EP2384837A3 (fr) 2012-04-04

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