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EP1538415A1 - Canal d'écoulement - Google Patents

Canal d'écoulement Download PDF

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Publication number
EP1538415A1
EP1538415A1 EP03027584A EP03027584A EP1538415A1 EP 1538415 A1 EP1538415 A1 EP 1538415A1 EP 03027584 A EP03027584 A EP 03027584A EP 03027584 A EP03027584 A EP 03027584A EP 1538415 A1 EP1538415 A1 EP 1538415A1
Authority
EP
European Patent Office
Prior art keywords
fluid
channel
flow
heat exchanger
flow channel
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Withdrawn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
EP03027584A
Other languages
German (de)
English (en)
Inventor
Miroslav Dr. Podhorsky
Wolfgang Schug
Wolfgang Holten
Hans-Georg Schrey
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.)
Balcke Duerr GmbH
Original Assignee
Balcke Duerr 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 Balcke Duerr GmbH filed Critical Balcke Duerr GmbH
Priority to EP03027584A priority Critical patent/EP1538415A1/fr
Priority to EP04028245A priority patent/EP1557627A1/fr
Priority to US10/998,828 priority patent/US20050211424A1/en
Priority to CN201010110676A priority patent/CN101846478A/zh
Priority to CN200410096811.2A priority patent/CN1624413A/zh
Publication of EP1538415A1 publication Critical patent/EP1538415A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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

Definitions

  • the present invention relates to a flow channel with a channel wall to Guiding a flowing fluid, and a heat exchanger with such Channel. Furthermore, the invention relates to an air condenser for the condensation of Water vapor, in particular turbine steam of a power plant, wherein condensing steam via a steam supply line and distribution lines the Heat exchangers can be fed, and with lines for condensate removal and Inertgasabtechnisch are provided.
  • fluids are used for storage and storage Transport of heat used.
  • the Fluid heat supplied wherein the fluid via a channel system to another Is promoted where the appropriate thermal output provided shall be.
  • another device that it allows the heat to escape from the fluid.
  • Such devices are as Heating walls, heat exchangers or the like.
  • Such a device usually has a flow channel, which of the fluid can be flowed through. The wall of the channel serves beside the guidance of the flowing one Fluids also for heat exchange with the fluid.
  • Known channel arrangements include, for example, walls with smooth surfaces to oppose as little resistance to the flowing fluid as possible. So can be the energy required to keep the fluid flowing To be kept low. Usually forms at the Channel wall in the flow direction substantially laminar flow, so that a heat exchange between the fluid and the channel wall substantially only with the part of the flow that flows near the channel wall. One Most of the fluid provided by the heat capacity can not be used become.
  • Heat exchangers with generic flow channels are often in Range of power plants used to from a fluid, which a Has undergone thermal power process to recover remaining energy and to make usable. Among other things, it is common and desirable to do this At least partially recycle energy to the process or otherwise to increase the effectiveness of the process. Especially Advantageously, such heat exchangers are used in air condensers, such as For example, to recover the heat energy from a Turbine steam can be used.
  • the optimal performance of a heat exchanger depends not only on the transferable heat output, but also on the power required is to carry out the fluids through the heat exchanger. To this To keep power output as low as possible, is within the channel system of Heat exchanger a largely laminar flow desirable because this too low flow losses can lead. This results in addition, that as few deflections of the fluid should take place. It stands contrary, that a laminar flow considerably less Heat exchange allows as a turbulent flow. The well-known Heat exchangers only partially meet these requirements.
  • Heat exchangers due to their essentially laminar flow have a low pressure drop, usually allow only one low heat exchange, so that much of the energy of the first through flowing fluid is lost.
  • heat exchangers the due to its substantially turbulent flow, a high pressure drop to a supply of the first fluid at a high pressure reliant.
  • it is necessary to have appropriate funds for Provide pressure increase such as compressors, pumps or the like.
  • the present invention is therefore based on the object , a generic flow channel in such a way that at a low pressure drop, a high heat transfer rate is made possible by a fluid to the channel wall.
  • the present invention proposes a flow channel having a channel wall for guiding a flowing fluid, wherein heat is exchangeable between the fluid and the channel wall, and wherein the channel wall has a structured surface at least partially on the side facing the fluid.
  • the structured surface can be achieved that the turbulence of the flow is increased in the region of the channel wall, which allows increased heat transfer.
  • a fluidic Boundary layer can be reduced.
  • the turbulence can be so low be held that thereby the pressure drop at the flow channel not is significantly increased.
  • the structured surface for example, by the Channel wall itself or be formed by a coating.
  • the channel wall may have an embossing that defines the textured surface forms.
  • the channel wall or a coating of the channel wall can one high coefficient of friction to the fluid to the required turbulence to reach.
  • the characteristics of the canal wall and the type of structured Surface are advantageous to the fluid provided for the flow coordinated to achieve the best possible effect. So can For example, in a highly viscous fluid, a very fine surface structure be provided, while in a low-viscosity fluid a coarse Surface structure may be provided. Furthermore, the Flow rate of the fluid to take into account the influence on the may have a textured surface.
  • the structured surface may be partially be provided on the fluid side facing. But you can also over the entire channel length and / or over the entire circumference of the channel Flow channel may be provided. Advantageously, it is arranged in the places where the heat transfer is particularly important. So can the Flow channel in an area intended only to convey the fluid is, have a smooth surface, whereas in an area of provided heat exchange provided a surface according to the invention is. Unwanted heat losses can be kept low.
  • the textured surface has moldings. These formations are advantageously formed in the channel wall and protrude into the flow channel. An enlargement of the surface of the channel wall can be achieved. The Size, the number and also the arrangement of the formations to each other so be chosen that the influence on the pressure drop in this flow channel is largely negligible. At the same time, the formations effect Turbulence of the fluid flows in the region of the channel wall. This surface is inexpensive to produce by known means.
  • the structured surface depressions having.
  • the wells can as well as with the formations a Increasing the turbulence of the fluid flow achieved in the region of the channel wall become. Further enlargement of the surface can be achieved.
  • a channel wall with wells very inexpensive to produce by this For example, by a corresponding embossing tool, which on the Channel wall runs, is produced.
  • the formations and / or depressions to form a uniform pattern.
  • the formations and / or recesses offset from one another in the flow direction.
  • the shape of the molding and / or depression can be used to achieve a optimal heat transfer performance can be adjusted. So the shape For example, by a ball section, cone section, a pyramid or be formed.
  • the Deviation of the formation and / or depression from a centerline of the Fluid facing surface of the channel wall is a few tenths of a millimeter.
  • an increase in the pressure drop can be further reduced.
  • thermotechnical connection in at least one of the flow channels thermally conductive, aligned in the longitudinal direction of the flow channel, flowed through meandering structure, which is at least partially at their meandering turning points with an adjacent plate in thermotechnical connection stands.
  • an increase in the heat transferring surface can be achieved.
  • the Meander structure also be provided with a structured surface, whereby a further increase of the heat transfer performance can be achieved can.
  • the thermal connection can be achieved by soldering, welding, gluing or the like may be formed.
  • the invention further provides a heat exchanger with fluids through which it is possible to flow Flow channels proposed to each other in thermo-technical Active compound, wherein at least one flow channel according to the invention is provided.
  • the heat transfer performance of a Heat exchanger can be increased without significantly increasing its design must be and / or a higher pressure drop is recorded. So can advantageous also subsequently in an existing plant an inventive Heat exchanger with a higher heat transfer capacity retrofitted without requiring a larger space.
  • a smaller design of the heat exchanger to gain space in an existing facility for example. Due to the substantially same pressure drop can be achieved that In terms of equipment, further measures can be avoided, such as for example, providing an additional compressor or the like.
  • by means of the structured surface not only the rigidity be increased hereby provided flow channel, but also the entire heat exchanger. This can thus be an enlarged mechanical Withstand stress.
  • the flow channels at least partially a form plate-shaped channel arrangement.
  • the heat exchanger a Having a plurality of stacked plate-shaped channel arrangements, wherein neighboring plate-shaped channel arrangements alternately from one different fluid can be flowed through. So can with the good adaptability Stacking at the same time a high heat transfer performance of a fluid to a second fluid, which flow through different channel arrangements, be achieved.
  • the first fluid is formed by air. Air is inexpensive and easily deployable by known means.
  • the second fluid by water vapor is formed.
  • Water vapor contains a lot of energy, caused by cooling and Condensation can be recovered. A high energy yield can be achieved.
  • the invention further provides an air condenser for the condensation of Steam, in particular turbine steam of a power plant, proposed, wherein steam to be condensed via a steam supply line and distributions the heat exchangers can be supplied, and wherein lines for condensate removal and Inertgasabtechnisch are provided, wherein the heat exchanger a inventive heat exchanger.
  • an air condenser for the condensation of Steam, in particular turbine steam of a power plant, proposed, wherein steam to be condensed via a steam supply line and distributions the heat exchangers can be supplied, and wherein lines for condensate removal and Inertgasabtechnisch are provided, wherein the heat exchanger a inventive heat exchanger.
  • a high Heat transfer performance can be achieved.
  • the air condenser can therefore a have smaller design and are produced more cheaply.
  • the air condenser Nature train cooling tower is.
  • the cooling tower can turn out smaller, thereby the intervention in the environment can be reduced.
  • Fig. 1 shows a heat exchanger 10 according to the invention with a channel 14 and Flow channels 12, which can be flowed through in crossflow.
  • the flow channel 14 is traversed by water vapor, while the flow channels 12 of air be flowed through.
  • Flow channels 12 and 14 are separated from each other arranged.
  • Flow channel 14 is formed as a wide, shallow channel consisting of two parallel spaced planes arranged for Formation of the closed channel 14 laterally connected to semicircular profiles are.
  • the flow channels 12, 14 form a plate-shaped channel arrangement 16.
  • Several such heat exchangers 10 can form a stack one above the other be arranged.
  • Such heat exchanger plate stacks can be stored in a cooling tower, in particular a natural draft cooling tower, be arranged.
  • thermo-technical Connection executed as an adhesive connection.
  • the thermal connection may also be formed as a solder or welded connection.
  • the Metal band is made of stainless steel.
  • the channel wall 18 of the flow channel 14 has on its inside a structured surface 20, as shown in Fig. 2.
  • the structured Surface 20 is provided with formations 22 and recesses 24, which are the Having a shape of a spherical section.
  • Formations 22 and recesses 24 are arranged, which has a uniform pattern form. Shapes 22 and recesses 24 are spaced and offset arranged to each other.
  • FIG. 4 shows the arrangement on the channel wall 18 in section along a line IV - IV in Fig. 2.
  • the deviation from the center line 28 is in the present example about 0.3 mm.
  • FIG. In this Design are in the flow direction in pairs successive Formations 22 and recesses 24 are provided, the one another have a large distance.
  • the basic form is by a truncated pyramid in the formed substantially rectangular base.
  • the deviation from the centerline is about 0.07 mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP03027584A 2003-12-01 2003-12-01 Canal d'écoulement Withdrawn EP1538415A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP03027584A EP1538415A1 (fr) 2003-12-01 2003-12-01 Canal d'écoulement
EP04028245A EP1557627A1 (fr) 2003-12-01 2004-11-29 Canal d'écoulement
US10/998,828 US20050211424A1 (en) 2003-12-01 2004-11-30 Duct
CN201010110676A CN101846478A (zh) 2003-12-01 2004-12-01 管道
CN200410096811.2A CN1624413A (zh) 2003-12-01 2004-12-01 管道

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03027584A EP1538415A1 (fr) 2003-12-01 2003-12-01 Canal d'écoulement

Publications (1)

Publication Number Publication Date
EP1538415A1 true EP1538415A1 (fr) 2005-06-08

Family

ID=34442924

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03027584A Withdrawn EP1538415A1 (fr) 2003-12-01 2003-12-01 Canal d'écoulement

Country Status (3)

Country Link
US (1) US20050211424A1 (fr)
EP (1) EP1538415A1 (fr)
CN (2) CN1624413A (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100690891B1 (ko) * 2005-05-26 2007-03-09 엘지전자 주식회사 건조기용 열교환기 및 이를 이용한 응축식 건조기
US9302337B2 (en) * 2012-08-09 2016-04-05 Modine Manufacturing Company Heat exchanger tube, heat exchanger tube assembly, and methods of making the same
CN103093929B (zh) * 2013-01-27 2015-10-28 大连世有电力科技有限公司 变压器呼吸器用的冷凝罩
CN104533538A (zh) * 2014-12-15 2015-04-22 厦门大学 一种带肋结构的换热流道壁
CN108590776A (zh) * 2018-04-24 2018-09-28 厦门大学 一种使用三棱锥涡流发生器的涡轮叶片冷却方法

Citations (14)

* Cited by examiner, † Cited by third party
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US3684007A (en) * 1970-12-29 1972-08-15 Union Carbide Corp Composite structure for boiling liquids and its formation
US4258783A (en) * 1977-11-01 1981-03-31 Borg-Warner Corporation Boiling heat transfer surface, method of preparing same and method of boiling
JPS6029593A (ja) * 1983-07-27 1985-02-14 Hitachi Ltd 単相流伝熱管構造
JPS6066096A (ja) * 1983-09-20 1985-04-16 Matsushita Electric Ind Co Ltd 伝熱管
JPS6066097A (ja) * 1983-09-20 1985-04-16 Matsushita Electric Ind Co Ltd 伝熱管
JPS6115088A (ja) * 1984-06-28 1986-01-23 Matsushita Electric Ind Co Ltd 沸騰用伝熱管
FR2569263A1 (fr) * 1976-08-11 1986-02-21 Escher Wyss Gmbh Echangeur de chaleur comportant des cloisons a surfaces structurees
JPS61175485A (ja) * 1985-01-30 1986-08-07 Kobe Steel Ltd 伝熱管及びその製造方法
JPS61175486A (ja) * 1985-01-31 1986-08-07 Matsushita Electric Ind Co Ltd 沸騰用伝熱管
US5681661A (en) * 1996-02-09 1997-10-28 Board Of Supervisors Of Louisiana State University And Agricultural And Mechanical College High aspect ratio, microstructure-covered, macroscopic surfaces
US5697430A (en) * 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
EP0819908A2 (fr) * 1996-07-19 1998-01-21 Alcan Alluminio S.p.A. Section laminée pour échangeur de chaleur et méthode de production
US6173762B1 (en) * 1993-07-07 2001-01-16 Kabushiki Kaisha Kobe Seiko Sho Heat exchanger tube for falling film evaporator
US6336501B1 (en) * 1998-12-25 2002-01-08 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Tube having grooved inner surface and its production method

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JPS56155391A (en) * 1980-04-30 1981-12-01 Nippon Denso Co Ltd Corrugated fin type heat exchanger
DE3238943A1 (de) * 1982-10-21 1984-04-26 kabelmetal electro GmbH, 3000 Hannover Waermetauscher, insbesondere fuer sonnenkollektoren
US5224538A (en) * 1991-11-01 1993-07-06 Jacoby John H Dimpled heat transfer surface and method of making same
US5377746A (en) * 1993-04-26 1995-01-03 Fintube Limited Partnership Texturized fin
AU1888595A (en) * 1994-03-03 1995-09-18 Gea Luftkuhler Gmbh Finned tube heat exchanger
US5738169A (en) * 1995-11-07 1998-04-14 Livernois Research & Development Co. Heat exchanger with turbulated louvered fin, manufacturing apparatus and method
KR100297189B1 (ko) * 1998-11-20 2001-11-26 황해웅 열전달촉진효과를갖는고효율모듈형오엘에프열교환기
JP3864916B2 (ja) * 2002-08-29 2007-01-10 株式会社デンソー 熱交換器

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3684007A (en) * 1970-12-29 1972-08-15 Union Carbide Corp Composite structure for boiling liquids and its formation
FR2569263A1 (fr) * 1976-08-11 1986-02-21 Escher Wyss Gmbh Echangeur de chaleur comportant des cloisons a surfaces structurees
US4258783A (en) * 1977-11-01 1981-03-31 Borg-Warner Corporation Boiling heat transfer surface, method of preparing same and method of boiling
JPS6029593A (ja) * 1983-07-27 1985-02-14 Hitachi Ltd 単相流伝熱管構造
JPS6066096A (ja) * 1983-09-20 1985-04-16 Matsushita Electric Ind Co Ltd 伝熱管
JPS6066097A (ja) * 1983-09-20 1985-04-16 Matsushita Electric Ind Co Ltd 伝熱管
JPS6115088A (ja) * 1984-06-28 1986-01-23 Matsushita Electric Ind Co Ltd 沸騰用伝熱管
JPS61175485A (ja) * 1985-01-30 1986-08-07 Kobe Steel Ltd 伝熱管及びその製造方法
JPS61175486A (ja) * 1985-01-31 1986-08-07 Matsushita Electric Ind Co Ltd 沸騰用伝熱管
US6173762B1 (en) * 1993-07-07 2001-01-16 Kabushiki Kaisha Kobe Seiko Sho Heat exchanger tube for falling film evaporator
US5697430A (en) * 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US5681661A (en) * 1996-02-09 1997-10-28 Board Of Supervisors Of Louisiana State University And Agricultural And Mechanical College High aspect ratio, microstructure-covered, macroscopic surfaces
EP0819908A2 (fr) * 1996-07-19 1998-01-21 Alcan Alluminio S.p.A. Section laminée pour échangeur de chaleur et méthode de production
US6336501B1 (en) * 1998-12-25 2002-01-08 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Tube having grooved inner surface and its production method

Also Published As

Publication number Publication date
CN1624413A (zh) 2005-06-08
CN101846478A (zh) 2010-09-29
US20050211424A1 (en) 2005-09-29

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