EP2192368A2 - Echangeur thermique - Google Patents

Echangeur thermique Download PDF

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Publication number
EP2192368A2
EP2192368A2 EP20090177527 EP09177527A EP2192368A2 EP 2192368 A2 EP2192368 A2 EP 2192368A2 EP 20090177527 EP20090177527 EP 20090177527 EP 09177527 A EP09177527 A EP 09177527A EP 2192368 A2 EP2192368 A2 EP 2192368A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
tube
flow
heat transfer
transfer medium
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.)
Withdrawn
Application number
EP20090177527
Other languages
German (de)
English (en)
Inventor
Dirk Drews
Frank Schubert
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.)
SolarHybrid AG
Original Assignee
SolarHybrid AG
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 SolarHybrid AG filed Critical SolarHybrid AG
Publication of EP2192368A2 publication Critical patent/EP2192368A2/fr
Withdrawn legal-status Critical Current

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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
    • F28D7/02—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
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • 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
    • F28F1/122—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 being formed of wires
    • 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
    • F28F1/26—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 being integral with the element

Definitions

  • the invention relates to a heat exchanger for exchanging heat between a first and a second heat transfer medium, with a flow through the first heat transfer medium flow channel and a flow through the second heat transfer medium heat exchanger tube, which is arranged overflow within the flow channel of the first heat transfer medium.
  • Heat exchangers with guided in a flow channel heat exchanger tubes are used in heat supply systems for the transfer of heat energy between two heat transfer media, for example between two water circuits, between a steam cycle and a hot water circuit or between a refrigerant circuit and a hot water circuit.
  • one of the two heat transfer media is guided in a flow channel and the second heat transfer medium mostly out of the opposite direction in a heat exchanger tube within the flow channel of the first heat transfer medium.
  • a heat exchange between the two heat transfer media takes place.
  • the object of the invention is to provide a heat exchanger in which the heat transfer from the first heat transfer medium to the heat exchanger tube and thus the heat transfer from the first heat transfer medium to the second heat transfer medium is improved.
  • the means for supporting turbulent flows turbulence of the first heat transfer medium between the heat exchanger tube and the channel wall of the flow channel are specifically supported. Due to these turbulence effects, the laminar boundary layers on the jacket of the heat exchanger tube are detached, resulting in a better heat transfer from the first heat transfer fluid to the heat exchanger tube. In addition, due to adhesion forces, the first heat transfer medium tends to be laminar against the jacket of the heat exchanger tube, whereby the first heat transfer fluid is also directed away from the heat exchanger tube in its flow direction, so that large parts of the circumference of the heat exchanger tube contribute to heat transfer.
  • the support means form bottlenecks in the flow-through cross-section of the flow channel.
  • the area of bottlenecks there is a change in the flow velocity of the first heat transfer medium.
  • the heat transfer medium is accelerated rapids and then delayed after passing the constriction, which forms within the flow of the first heat transfer fluid pulses that continue undulating and counteract the formation of laminar layers on the shell of the heat exchanger tube.
  • the support means by a structuring of the shell of the heat exchanger tube be formed. This results in a mounting-friendly design of the heat exchanger, wherein the support means are integrally provided on the jacket of the heat exchanger tube. It is not necessary to arrange separate elements in the area between the jacket of the heat exchanger tube and a channel wall of the flow channel.
  • the heat exchanger tube is a corrugated tube whose waves form the support means.
  • Corrugated pipes are characterized by an inner and outer wavy contour of the tubular body, wherein the outer shafts form a support for the formation of turbulent outer flows of the first heat transfer medium in the region between the heat exchanger tube and a wall of the flow channel.
  • the inner shafts form a support for the formation of turbulent outer flows of the first heat transfer medium in the region between the heat exchanger tube and a wall of the flow channel.
  • a turbulent flow of the second heat transfer medium is achieved, so that form on the inner surface of the heat exchanger tube no heat transfer affecting laminar boundary layers.
  • Such a configuration is particularly advantageous when the first and the second heat transfer medium are liquid.
  • stainless steel corrugated pipes in particular are advantageous due to the hygienically advantageous properties of stainless steel in the service water sector.
  • a further embodiment provides that the heat exchanger tube is a finned tube whose ribs form the support means. Similar to the outer shafts of a corrugated tube, the ribs support the formation of a turbulent outer flow of the first heat transfer medium. In contrast to a corrugated tube, however, the inner surface of conventional finned tubes is flat, so that on the inside of the corrugated tube no support means for the formation of turbulent internal flows are provided. This embodiment is particularly suitable when a vaporous heat transfer medium is guided in the heat exchanger tube, as is the case for example with refrigerant circuits.
  • the support means bear against one of the two channel walls such that passage openings form.
  • the passage openings form bottlenecks of the flow cross section of the first heat transfer fluid, resulting in nozzle-like bottlenecks with the associated, laminar boundary layers dissolving speed differences.
  • the support means are formed by flow obstacles.
  • the flow obstacles can be arranged in the region between the heat exchanger tube and a channel wall of the flow channel to reduce the flow cross section. This also results in bottlenecks in the flow path of the first heat transfer medium, which promote the formation of turbulence and solve laminar layers.
  • the flow obstacles are part of a wire mesh, which is arranged in the region between the heat exchanger tube and a channel wall of the flow channel.
  • the flow of the first heat transfer fluid is accelerated and deflected due to the cross-sectional reduction, which can be avoided laminar boundary layers on the jacket of the heat exchanger tube.
  • the flow channel is annular-cylindrical, wherein an inner channel wall is formed by an inner tube and an outer channel wall of an outer tube.
  • the annular cylindrical channel is used as a flow channel for the first heat transfer medium.
  • the heat exchanger tube extends helically around the inner tube through the flow channel, resulting in long flow paths of the second heat transfer medium within the heat exchanger tube and the associated, efficient heat transfer from one to the other heat transfer medium.
  • the inner tube is made of a rigid material, so that the flexible heat exchanger tube can be wound helically around the inner tube.
  • the outer tube of a flexible material in particular of film material of suitable thickness exists.
  • the flexible material of the outer tube can be placed close to the radially outer support means and then tightened for example via straps, so that there is a close contact of the support means on the two channel walls of the flow channel.
  • the outer tube may be formed from a tube, for example plastic tube, which is divided longitudinally in two halves prior to assembly, the halves are positioned around the heat exchanger tube and then joined together by suitable methods, for example by welding.
  • suitable methods for example by welding.
  • the flow channel and the heat exchanger tube are arranged in a common pressure chamber, which allows a structurally favorable guidance of the two streams of heat transfer media.
  • the inner tube, the outer tube and the heat exchanger tube form a structural unit which can be inserted into the pressure chamber.
  • the assembly of inner tube, outer tube and heat exchanger tube and the associated inlet and outlet ports for the heat transfer media can be pre-assembled in a first step and then used in a structural unit in the pressure chamber, resulting in a simple assembly.
  • the outer tube is sealed by a sealing element with respect to an inner surface of the pressure chamber and the inner tube is closed by a wall arranged below an inlet for the first heat carrier medium. This blocks unwanted flow paths. On the one hand, a flow between the outer tube and the inner surface of the pressure chamber is avoided. On the other hand it is avoided that a continuous flow forms inside the inner tube.
  • FIGS. 1 to 7 show different views of a heat exchanger 1, based on which below the structure of the heat exchanger 1 and the flow conditions in the interior of the heat exchanger 1 are first explained below.
  • the heat exchanger 1 is composed of an internal unit 40, which is arranged within a pressure chamber 20 sealed to the outside.
  • the pressure chamber 20 is of a total cylindrical geometry and is formed by a pressure cylinder 21, which is closed at the end face flange plates 22.
  • the assembly 40 is first preassembled and then inserted into the pressure cylinder 21, which may already be connected to one of the two flange plates 22. Subsequently, the second flange plate 22 is connected to the pressure cylinder 22, whereby the pressure chamber 20 is sealed to the outside.
  • the first heat transfer medium flows through a ring-cylindrical or tubular gap-shaped flow channel 4 in the exemplary embodiments, which is formed by a double tube formed from an inner tube 2 and a concentric outer tube 3 whose inner and outer lateral surfaces form the channel walls 7, 8 of the flow channel 4, cf. especially the FIGS. 6 and 7 ,
  • a ring-cylindrical or tubular gap-shaped flow channel 4 in the exemplary embodiments, which is formed by a double tube formed from an inner tube 2 and a concentric outer tube 3 whose inner and outer lateral surfaces form the channel walls 7, 8 of the flow channel 4, cf. especially the FIGS. 6 and 7 .
  • Within this annular cylindrical space flows the first heat transfer medium as shown in FIG FIG. 6 from top to bottom, wherein it overflows in the flow channel 4 helically around the inner tube 2 around extending heat exchanger tube 5.
  • the second heat transfer medium flows counter to the flow direction of the first heat transfer medium from bottom to top.
  • the two heat transfer media are at different temperature levels, an exchange of heat from one to the other heat transfer medium, so that the one heat transfer medium cooled the heat exchanger 1 and the other heat transfer medium leaves the heat exchanger 1 is heated.
  • the transfer of heat always takes place via the heat exchanger tube 5, but can be done in two directions.
  • the second, in the heat exchanger tube 5 guided heat transfer medium, for example domestic hot water, via the first, guided in the flow channel 4 heat transfer medium can be heated.
  • the changes in the density of the heat transfer media due to the temperature changes support the flows within the heat exchanger.
  • the cold entering the heat exchanger tube 5 in the lower second heat transfer medium is heated via the first heat transfer medium, whereby its density is reduced, so it is easier, and rises within the heat exchanger tube upwards.
  • the situation is different with the first heat transfer medium. This occurs at the top of the heat exchanger at a higher temperature.
  • the density of the first heat transfer medium increases, so that the flow of the first heat transfer medium cooling downwards is likewise supported due to the gravitational relationships within the flow passage 4. This results in a natural support of the currents due to the changing density ratios.
  • the transfer of heat can also be transferred in the opposite direction from the guided in the heat exchanger tube 5 heat transfer medium to the guided in the flow channel 4, the first medium, such as when the heat exchanger as a condenser used in heat pumps.
  • the flow directions are reversed to the above-described service water heating, ie the first heat transfer medium in the flow channel 4 upwards and the second heat transfer medium in the heat exchanger tube fifth flows down.
  • the first, higher-temperature heat transfer medium which may be, for example, heating water from a buffer memory occurs in accordance with the execution Fig. 6 via the inlet 23 in the inner region of the inner tube 2 a.
  • the first heat transfer medium meets a wall 28 closing the further flow path, which leads to a reversal of the direction of the flow of the first heat transfer fluid, cf. especially FIGS. 6 and 7 ,
  • the first heat transfer medium enters the annular cylindrical flow channel 4 in the upper region and leaves the heat exchanger 1 cooled over the outlet 24 after flowing over the helical heat exchanger tube 5.
  • the second less highly tempered Heat transfer medium in the heat exchanger tube 5 which may be, for example, water of a domestic hot water supply system.
  • the second heat transfer medium rises in the heat exchanger tube 5 helically in the flow channel 4 upwards and exits heated via the outlet 26 from the heat exchanger.
  • a sealing element 27 is provided between the outer tube 3 and an inner wall 29 of the pressure cylinder 21.
  • FIGS. 1 to 6 the support means 10, 11, 12 according to the invention are not shown for illustration, can form in the cladding region of the heat exchanger tube 5 laminar boundary layers of the first heat transfer medium surrounding the surface of the heat exchanger tube 5 similar to an oil film and the heat transfer from the first heat transfer medium to that in the heat exchanger tube 5 flow affecting second heat transfer medium.
  • 4 flow points of the first heat transfer medium in the region between the helices of the heat exchanger tube 5 can form when flowing through the flow channel, whereby the heat transfer is also impaired.
  • support means 10, 11, 12 are provided for supporting or forming turbulent flows between the heat exchanger tube 5 and the channel walls 7, 8 of the annular cylindrical flow channel 4, which are integrally formed on the jacket of the heat exchanger tube 5 and or as separate components, what follows from the FIGS. 8 to 26 will be explained in detail.
  • FIGS. 8 to 11 a section of a heat exchanger tube 5 according to a first embodiment of the heat exchanger 1 is shown.
  • the heat exchanger tube 5 is formed as a corrugated pipe, for example, as a drinking water-approved stainless steel corrugated pipe.
  • the waves of the corrugated pipe form the means 10 for supporting turbulent flows, which subsequently with the aid of FIGS. 16 to 18 will be explained.
  • Fig. 16 is a plan view of the heat exchanger 1 and in particular the helically through the annular cylindrical flow channel 4 between the inner tube 2 and the outer tube 3 extending through heat exchanger tube 5 shown.
  • the heat exchanger tube 5 is of a corrugated tube as shown in the FIGS. 8 to 11 formed and has according to the representations in the FIGS. 8 to 11 a wavy outer contour whose waves 10 form means for supporting a turbulent flow.
  • the wave crests of the shafts 10 bear against the inner tube 2 and the outer tube 3. This results in the troughs through openings 9, which are flowed through by the first heat transfer medium as it flows through the flow channel 4.
  • FIGS. 12 to 15 show a portion of an alternatively designed heat exchanger tube 5, on the circumference of ribs 11 are arranged, whereas the interior of the heat exchanger tube 5 is formed smooth surface. While in a heat exchanger tube 5 according to the FIGS. 8 to 11 Even in the interior of the heat exchanger tube 5 or in the second heat transfer fluid turbulence are generated, this is in a heat exchanger tube 5 according to the FIGS. 8 to 11 only in the first, the heat exchanger tube 5 flowing around the heat transfer medium of the case. In the in the FIGS. 12 to 15
  • the heat exchanger tube shown is in particular a copper finned tube.
  • Such a tube lends itself when inside the heat exchanger tube 5, a vaporous or located in phase transitions heat transfer medium, for example, refrigerant a heat pump is performed, since at the phase transitions boiling or condensation or evaporation or liquefaction, the heat transfer through laminar boundary layers less impaired becomes.
  • the support means 10, 11 are integral part of the outer surface of the heat exchanger tube 5, show the FIGS. 19 to 23 an embodiment in which the support means 12 are formed by additional, introduced in the region between the heat exchanger tube 5 and a channel wall 7, 8 flow obstacles.
  • Fig. 19 Like the perspective view in Fig. 19 can recognize, it concerns with the support means to flow obstacles 12, which represent bottlenecks within the flow channel 4.
  • the flow obstacles 12 are formed by a kind of wire basket 13, wherein the first heat transfer medium is deflected and accelerated when flowing over the mesh of the wire basket 13, whereby the laminar boundary layers on the heat exchanger tube 5 can also be removed.
  • the support means 12 are provided both in the region between the inner tube 4 and the heat exchanger tube 5, as well as in the region between the heat exchanger tube 5 and the outer tube 3 as fitting to the channel walls 7, 8 intermediate layer, see. also Fig. 23 ,

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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)
EP20090177527 2008-11-30 2009-11-30 Echangeur thermique Withdrawn EP2192368A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810059543 DE102008059543A1 (de) 2008-11-30 2008-11-30 Wärmetauscher

Publications (1)

Publication Number Publication Date
EP2192368A2 true EP2192368A2 (fr) 2010-06-02

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ID=41719308

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20090177527 Withdrawn EP2192368A2 (fr) 2008-11-30 2009-11-30 Echangeur thermique

Country Status (2)

Country Link
EP (1) EP2192368A2 (fr)
DE (1) DE102008059543A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103712486A (zh) * 2013-12-18 2014-04-09 中国海洋石油总公司 同一流路中变水力直径的微通道扁管缠绕式换热器
WO2015144693A1 (fr) * 2014-03-25 2015-10-01 Vetco Gray Scandinavia As Agencement d'échangeur de chaleur sous-marin et procédé permettant d'améliorer l'efficacité de dissipation de chaleur dans un échangeur de chaleur sous-marin
CN112577338A (zh) * 2020-12-30 2021-03-30 乔治洛德方法研究和开发液化空气有限公司 内部安置有换热设备的高温流体运输管道，适用的换热设备及换热方法
EP3757485A4 (fr) * 2018-02-24 2021-10-27 Sanhua Holding Group Co., Ltd. Séparateur gaz-liquide et système d'échange de chaleur

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009011715A1 (de) 2009-03-09 2010-09-16 Solarhybrid Ag Hydraulische Weiche zum Anschluss von Wärmeerzeugern an eine Heizungsanlage, Heizungsanlage und Verfahren zum Betrieb einer Heizungsanlage
DE202009003113U1 (de) 2009-03-09 2010-07-29 Solarhybrid Ag Hydraulische Weiche zum Anschluss von Wärmeerzeugern an eine Heizungsanlage und Heizungsanlage mit einer hydraulischen Weiche
DE102010037206A1 (de) 2010-08-27 2012-03-01 Solarhybrid Ag Wärmetauscher
CN102313404B (zh) * 2011-09-05 2013-06-05 华北电力大学 一种分液式螺旋管结构的冷凝器
DE102014207660A1 (de) * 2014-04-23 2015-10-29 Mahle International Gmbh Innerer Wärmeübertrager

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Publication number Priority date Publication date Assignee Title
DE8134278U1 (de) * 1981-11-25 1982-04-15 Kühlerfabrik Längerer & Reich GmbH & Co KG, 7024 Filderstadt Waermeaustauscher
FR2686408B1 (fr) * 1992-01-16 1998-01-30 Anjou Sa Piscine Service Echangeur de chaleur utilise pour le rechauffement d'un fluide secondaire tel que de l'eau de piscine ou de l'eau de mer.
ES2306214T3 (es) * 2004-07-22 2008-11-01 P.S.A. Intercambiador de calor de serpentin (es) y nervadura(s) helicoidal (es) de separacion.
DE102006017432B4 (de) * 2006-04-06 2009-05-28 Visteon Global Technologies Inc., Van Buren Innerer Wärmeübertrager mit kalibriertem wendelförmigen Rippenrohr
DE102006031197B4 (de) * 2006-07-03 2012-09-27 Visteon Global Technologies Inc. Innerer Wärmeübertrager mit Akkumulator

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103712486A (zh) * 2013-12-18 2014-04-09 中国海洋石油总公司 同一流路中变水力直径的微通道扁管缠绕式换热器
CN103712486B (zh) * 2013-12-18 2015-12-16 中国海洋石油总公司 同一流路中变水力直径的微通道扁管缠绕式换热器
WO2015144693A1 (fr) * 2014-03-25 2015-10-01 Vetco Gray Scandinavia As Agencement d'échangeur de chaleur sous-marin et procédé permettant d'améliorer l'efficacité de dissipation de chaleur dans un échangeur de chaleur sous-marin
EP3757485A4 (fr) * 2018-02-24 2021-10-27 Sanhua Holding Group Co., Ltd. Séparateur gaz-liquide et système d'échange de chaleur
US11573036B2 (en) 2018-02-24 2023-02-07 Sanhua Holding Group, Co., Ltd. Gas-liquid separator and heat exchange system
CN112577338A (zh) * 2020-12-30 2021-03-30 乔治洛德方法研究和开发液化空气有限公司 内部安置有换热设备的高温流体运输管道，适用的换热设备及换热方法
US11940228B2 (en) 2020-12-30 2024-03-26 L'Air Liquide, Société Anonyme pour l'Etude et l'Exploitation des Procédés Georges Claude High-temperature fluid transporting pipeline with heat exchange apparatus installed therein, suitable heat exchange apparatus and heat exchange method

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