EP0417428A2 - Echangeur de chaleur à faisceau tubulaire - Google Patents

Echangeur de chaleur à faisceau tubulaire Download PDF

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Publication number
EP0417428A2
EP0417428A2 EP90113566A EP90113566A EP0417428A2 EP 0417428 A2 EP0417428 A2 EP 0417428A2 EP 90113566 A EP90113566 A EP 90113566A EP 90113566 A EP90113566 A EP 90113566A EP 0417428 A2 EP0417428 A2 EP 0417428A2
Authority
EP
European Patent Office
Prior art keywords
cooling channels
heat exchanger
tube
tubes
jacket
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
EP90113566A
Other languages
German (de)
English (en)
Other versions
EP0417428B1 (fr
EP0417428A3 (en
Inventor
Peter Brücher
Helmut Lachmann
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.)
Deutsche Babcock Borsig AG
Original Assignee
Deutsche Babcock Borsig 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6389119&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0417428(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Deutsche Babcock Borsig AG filed Critical Deutsche Babcock Borsig AG
Priority to AT90113566T priority Critical patent/ATE95303T1/de
Publication of EP0417428A2 publication Critical patent/EP0417428A2/fr
Publication of EP0417428A3 publication Critical patent/EP0417428A3/de
Application granted granted Critical
Publication of EP0417428B1 publication Critical patent/EP0417428B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/0229—Double end plates; Single end plates with hollow spaces
    • 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
    • F28D2021/0075—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for syngas or cracked gas cooling systems

Definitions

  • the invention relates to a tube bundle heat exchanger with the features of the preamble of patent claim 1.
  • Such tube-bundle heat exchangers serve as process gas waste heat boilers for the rapid cooling of reaction gases from cracking furnaces or chemical plant reactors with simultaneous generation of high-pressure steam as a heat-dissipating medium.
  • the tube plate arranged on the gas inlet side is thin compared to the tube plate on the gas outlet side (DE-C-1 294 981, AT-B-361 953) .
  • the thin tube plate is stiffened by support plates which are arranged at a distance from the tube plate and are connected to it by anchors.
  • the thin tube plate is supported on a support plate via welded-in support fingers.
  • the space between the support plate and the tube plate is flowed through by cooling medium which is supplied through an annular chamber and enters the heat exchanger through annular gaps between the tubes and the support plate.
  • the cooling medium can be guided across the thin tube plate.
  • This water flow ensures good cooling of the tube plate and generates a high flow rate, which prevents deposits of particles from the cooling medium on the tube plate.
  • This double bottom has proven itself in operation, but its production is relatively complex.
  • the thick tube plate of a shell-and-tube heat exchanger of the generic type AT-B-361 953 arranged on the gas outlet side with cooling channels.
  • the cooling channels are arranged between the rows of tubes and at a relatively large distance from one another and from the side of the tube plate which comes into contact with the gas. The cooling of the tube plate effected by this arrangement of the cooling channels is just sufficient to control the gas temperatures on the gas outlet side of the heat exchanger.
  • the invention has for its object to form a cooled tube plate of the generic tube bundle heat exchanger such that with a small wall thickness on the gas side and high flow rate of the cooling medium, a uniform cooling medium distribution is achieved and that gas temperatures of more than 1,000 degrees C can be controlled.
  • the tube plate according to the invention can be made thick overall and thus meet the requirement to withstand the high pressure of the cooling medium. Because the tubes penetrate the cooling channels and thus run straight along a row of tubes, the cooling channels can be laid close together so that the cooling medium flows over a large area. The channel base with a constant wall thickness avoids material accumulation on the inside of the channel. Both lead to such intensive cooling of the tube plate that high gas temperatures of more than 1,000 degrees C can be mastered.
  • the speed of the cooling medium in the cooling channels can be set to such a value that particles which may be contained in the cooling medium cannot be deposited, so that there is no risk of the tube plate overheating.
  • a thin base part can thus be formed on the gas inlet side of the tube plate and is supported on a thick base part of the tube plate via the webs remaining between the cooling channels. This support is less expensive than support using individual anchors, which is reflected in a more even stress distribution.
  • the thin bottom part allows low-thermal cooling and enables a gap-free and high-quality execution of the welding of the pipes into the pipe plate.
  • the heat exchanger shown is used in particular for cooling cracked gas with the help of boiling and partially evaporating water under high pressure.
  • the heat exchanger consists of a tube bundle made up of individual tubes 1, through which the gas to be cooled flows and which are surrounded by a jacket 2. For the sake of clarity, only individual tubes 1 are shown.
  • the tubes 1 are held in two tube plates 3, 4, which are followed by a gas inlet 5 and a gas outlet 6 and which are welded into the jacket 2.
  • the tube plate 3 arranged on the gas inlet side is provided with cooling channels 7 running parallel to one another.
  • the cooling channels 7 are laid in the tube plate 3 such that, seen in the axial direction of the tube plate 3, the cooling channels 7 are at a smaller distance from the gas side of the tube plate 3 than from the inside of the jacket 2. In this way, a thin bottom part 8 pointing towards the gas side is created and a thicker bottom part 9 facing the jacket 2.
  • the cooling channels 7 according to FIGS. 1 to 6 are open on both sides and open into a chamber 10 which surrounds the tube plate 3 in a ring.
  • the inlet side of the chamber 10 is provided with one or more supply ports 11, via which the cooling medium under high pressure is supplied.
  • the cooling channels 7 can be guided through the tube plate 3 as cylindrical bores parallel to the plate surface. Subsequently, however, the initially circular cross-section is expanded by machining to a tunnel-shaped profile.
  • This tunnel-shaped cross-sectional shape is shown in the drawing and is characterized by a curved ceiling and by a flat sole 12 which runs parallel to the top of the tube plate 3. In this way, it is particularly easy to produce a thin base part with a constant wall thickness.
  • the side walls 13 of the tunnel-shaped cooling channels 7 are also flat and preferably run perpendicular to the sole 12. These side walls 13 form narrow webs 14, by means of which the thin bottom part 8 is supported on the thick bottom part 9 over a large support length.
  • the tube plate 3 is provided with bores 15 which are open to the interior of the jacket 2 and open into the cooling channels 7 perpendicular to their longitudinal extension. Through these recesses 15, the tubes 1 of the tube bundle are passed with play, forming an annular gap.
  • the tubes 1 of each row of tubes penetrate one of the cooling channels 7 and are welded into the thin bottom part 8 of the tube plate 3 by a fully welded seam 16 without a gap.
  • the width of the cooling channels 7 thus formed corresponds approximately to 1 to 2 times the value of the diameter of the tubes 1.
  • the cooling medium fed through the supply nozzle 11 into the inlet side of the chamber 10 enters the cooling channels 7 and partly enters the interior of the heat exchanger enclosed by the jacket 2 through the annular gaps between the tubes 1 and the bores 15. This part of the cooling medium rises along the outer sides of the tubes 1 in the jacket 2 and emerges as high-pressure steam from an outlet connection 17 welded into the jacket 2.
  • the amount of cooling medium that does not enter the interior of the heat exchanger through the annular gaps leaves the cooling channels 7 on the opposite side and reaches the outlet side of the chamber 10.
  • the outlet side is separated from the inlet side by two partition walls 22 which are in the chamber 10 perpendicular to the longitudinal axis of the cooling channels 7 are arranged and extend over the entire cross section of the chamber 10.
  • one end of each cooling channel 7 is connected to the inlet side and the other end to the outlet side.
  • a pipe bend 23 is connected to the outlet side of the chamber 10 and opens into the interior of the heat exchanger. Through the pipe bend 23, the remaining amount of cooling medium enters the heat exchanger and is also converted into high pressure steam. This transfer of a partial cooling medium quantity ensures that a sufficiently high flow rate of the cooling medium also prevails at the outlet end of the cooling channels 7, so that no solid particles from the cooling medium can deposit on the base 12 of the cooling channels 7.
  • the flow resistance of the outer, shorter cooling channels 7 can be adapted to the flow resistance of the central, longer cooling channels 7. This can be done in that the cross section of the external cooling channels 7 is smaller or that 7 throttling points are installed in these external cooling channels.
  • an internal inlet chamber 18 for the cooling medium is shown, which extends over half of the circumference of the heat exchanger.
  • the wall of this inlet chamber 18 is connected to the inner wall of the casing 2 and in the edge area to the tube plate 3.
  • the cooling channels 7 are closed at both ends by a cover 20 each.
  • a bore 19, 24 is provided, which are passed in the axial direction through the thicker bottom part 9 of the tube plate 3.
  • One bore 19 extends from the inlet chamber 18 and serves to supply the cooling medium into the cooling channels 7.
  • the other bore 24 opens into the interior of the heat exchanger and removes the remaining amount of the cooling medium, which is not caused by the annular gaps between the tubes 1 and the turns 15 emerges.
  • the cooling channels 7 can also be cut into the tube plate 3 as edge recesses.
  • the cooling channels 7 formed in this way can have a curved or a flat ceiling.
  • These edge recesses are covered by sheet metal strips 21 which are welded to the webs 14 remaining between the cooling channels 7.
  • the tubes 1 are welded into the sheet metal strips 21.
  • this embodiment requires an increased number of weld seams, which could lead to additional stresses and have a weakening effect, but may be easier to manufacture.

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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP90113566A 1989-09-09 1990-07-16 Echangeur de chaleur à faisceau tubulaire Expired - Lifetime EP0417428B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90113566T ATE95303T1 (de) 1989-09-09 1990-07-16 Rohrbuendel-waermetauscher.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3930205A DE3930205A1 (de) 1989-09-09 1989-09-09 Rohrbuendel-waermetauscher
DE3930205 1989-09-09

Publications (3)

Publication Number Publication Date
EP0417428A2 true EP0417428A2 (fr) 1991-03-20
EP0417428A3 EP0417428A3 (en) 1991-11-06
EP0417428B1 EP0417428B1 (fr) 1993-09-29

Family

ID=6389119

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90113566A Expired - Lifetime EP0417428B1 (fr) 1989-09-09 1990-07-16 Echangeur de chaleur à faisceau tubulaire

Country Status (12)

Country Link
US (1) US5035283A (fr)
EP (1) EP0417428B1 (fr)
JP (1) JP3129727B2 (fr)
KR (1) KR0145700B1 (fr)
CN (1) CN1018024B (fr)
AT (1) ATE95303T1 (fr)
AU (1) AU632607B2 (fr)
BR (1) BR9004567A (fr)
CA (1) CA2024900C (fr)
DD (1) DD297697A5 (fr)
DE (2) DE3930205A1 (fr)
RU (1) RU2011942C1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2273119A1 (fr) * 2009-06-02 2011-01-12 AGO AG Energie + Anlagen Convertisseur de piston liquide
WO2013122528A3 (fr) * 2012-02-13 2013-10-24 Prometheus Technologies Gmbh Échangeur de chaleur adapté pour la production de noir de carbone

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4404068C1 (de) * 1994-02-09 1995-08-17 Wolfgang Engelhardt Wärmetauscher
DE4407594A1 (de) * 1994-03-08 1995-09-14 Borsig Babcock Ag Wärmetauscher zum Kühlen von heißem Reaktionsgas
DE4416932C2 (de) * 1994-05-13 1997-10-16 Shg Schack Gmbh Wärmetauscher
DE4445687A1 (de) * 1994-12-21 1996-06-27 Borsig Babcock Ag Wärmetauscher zum Kühlen von Spaltgas
US5630470A (en) * 1995-04-14 1997-05-20 Sonic Environmental Systems, Inc. Ceramic heat exchanger system
US5813453A (en) * 1996-06-01 1998-09-29 Deutsche Babcock-Borsig Ag Heat exchanger for cooling cracked gas
SE510240C3 (sv) 1996-10-14 1999-05-25 Edmeston Ab Roervaermevaexlare med balkplatta indelad i ett antal kanaler
CZ286748B6 (cs) * 1998-07-24 2000-06-14 Petr Ing. Krčmář Způsob odstraňování kalů a zařízení k jeho provádění
DE19846481A1 (de) * 1998-10-09 2000-05-04 Christian Schneider Vorrichtung zum thermischen Behandeln und zum Antreiben eines gasförmigen Mediums
JP4451520B2 (ja) * 1999-11-08 2010-04-14 株式会社日本触媒 竪型熱交換器
NL1014916C2 (nl) * 2000-04-11 2001-10-12 Bronswerk Heat Transfer Bv Warmtewisselaar.
EP1298404B1 (fr) * 2001-09-26 2005-04-06 Bronswerk Heat Transfer B.V. Echangeur de chaleur
US7223822B2 (en) 2002-10-15 2007-05-29 Exxonmobil Chemical Patents Inc. Multiple catalyst and reactor system for olefin polymerization and polymers produced therefrom
KR101113341B1 (ko) * 2002-10-15 2012-09-27 엑손모빌 케미칼 패턴츠 인코포레이티드 올레핀 중합용 다중 촉매 시스템 및 이로부터 제조된중합체
US7700707B2 (en) 2002-10-15 2010-04-20 Exxonmobil Chemical Patents Inc. Polyolefin adhesive compositions and articles made therefrom
US7541402B2 (en) 2002-10-15 2009-06-02 Exxonmobil Chemical Patents Inc. Blend functionalized polyolefin adhesive
US7550528B2 (en) 2002-10-15 2009-06-23 Exxonmobil Chemical Patents Inc. Functionalized olefin polymers
KR101129917B1 (ko) * 2005-03-21 2012-03-27 주식회사 포스코 열교환기 자동세정장치
DE102005023956A1 (de) * 2005-05-20 2006-11-23 Universität Stuttgart Kompakter Totalverdampfer
WO2007144911A1 (fr) * 2006-06-14 2007-12-21 Villa Scambiatori S.R.L. Échangeur de chaleur
JP5077159B2 (ja) * 2008-09-10 2012-11-21 パナソニック株式会社 電気掃除機
US8672021B2 (en) 2010-02-12 2014-03-18 Alfred N. Montestruc, III Simplified flow shell and tube type heat exchanger for transfer line exchangers and like applications
CN102384046A (zh) * 2011-06-24 2012-03-21 清华大学 一种用于以co2为工质的强化地热系统中的能量转换系统
CN103517967B (zh) * 2011-07-14 2016-01-20 三菱日立电力系统株式会社 气体冷却器、气化炉及含碳燃料气化复合发电装置
KR200476519Y1 (ko) * 2013-11-29 2015-03-09 한전케이피에스 주식회사 열 교환기 튜브 플러그
DE102014018261A1 (de) * 2014-12-11 2016-06-16 Borsig Gmbh Quenchkühlsystem
CN107860144B (zh) * 2017-12-29 2019-10-08 湖南中大经纬地热开发科技有限公司 用于隧道地能开发的换热系统
IT201800020257A1 (it) 2018-12-20 2020-06-20 Hexsol Italy Srl Giunzioni per tubi a doppia parete in scambiatori di calore e scambiatori di calore e scambiatori con tali giunzioni
CN109708514A (zh) * 2019-03-12 2019-05-03 江苏欧迈格板式换热器制造有限公司 简易换热器端板
CN112782197A (zh) * 2021-01-06 2021-05-11 蚌埠凯盛工程技术有限公司 退火窑炸板在线监测装置
CN113155015A (zh) * 2021-03-24 2021-07-23 中国石油大学(华东) 一种管道运行期间的应变监测方法及系统
CN116877381A (zh) * 2023-09-07 2023-10-13 山西常村大成节能科技有限公司 一种具有节能改造功能的空压机及使用方法

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GB974590A (en) * 1962-08-15 1964-11-04 Kobe Steel Ltd Lined tube header and the like
AT361953B (de) * 1979-07-10 1981-04-10 Borsig Gmbh Rohrbuendel-waermeaustauscher

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US3356135A (en) * 1964-12-24 1967-12-05 Robert K Sayre Once-through steam generator with means to provide saturated feed water
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DE1953628B2 (de) * 1969-10-24 1973-05-24 L & C Steinmuller GmbH, 5270 Gum mersbach Rohrbuendel-waermeaustauscher
DE2818892C2 (de) * 1978-04-28 1988-12-22 Bronswerk B.V., Amersfoort Wärmeaustauscher zum Abkühlen heißer Gase
NL7905640A (nl) * 1978-09-14 1980-03-18 Borsig Gmbh Van een pijpenbundel voorziene warmtewisselaar.
JPS5931668B2 (ja) * 1978-09-25 1984-08-03 東レ株式会社 竪型固定管板式熱交換器
JPS6042843B2 (ja) * 1979-07-30 1985-09-25 東洋エンジニアリング株式会社 廃熱ボイラ−
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DE3533219C1 (de) * 1985-09-18 1986-11-13 Borsig Gmbh, 1000 Berlin Rohrbuendelwaermetauscher
DE3641710A1 (de) * 1986-12-06 1988-06-16 Uhde Gmbh Vorrichtung zum waermetausch zwischen einem einen nh(pfeil abwaerts)3(pfeil abwaerts)-konverter verlassenden kreislaufgas und wasser
DE3715713C1 (de) * 1987-05-12 1988-07-21 Borsig Gmbh Waermetauscher insbesondere zum Kuehlen von Spaltgasen
DE3715712C1 (de) * 1987-05-12 1988-07-21 Borsig Gmbh Waermetauscher insbesondere zum Kuehlen von Spaltgas

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1096127B (de) * 1957-12-21 1960-12-29 Babcock & Wilcox Dampfkessel Verbindung von Rohren mit einer dickwandigen Rohrplatte
GB974590A (en) * 1962-08-15 1964-11-04 Kobe Steel Ltd Lined tube header and the like
AT361953B (de) * 1979-07-10 1981-04-10 Borsig Gmbh Rohrbuendel-waermeaustauscher

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2273119A1 (fr) * 2009-06-02 2011-01-12 AGO AG Energie + Anlagen Convertisseur de piston liquide
WO2013122528A3 (fr) * 2012-02-13 2013-10-24 Prometheus Technologies Gmbh Échangeur de chaleur adapté pour la production de noir de carbone

Also Published As

Publication number Publication date
CA2024900C (fr) 1999-08-24
CN1018024B (zh) 1992-08-26
KR0145700B1 (ko) 1998-08-17
EP0417428B1 (fr) 1993-09-29
CN1050928A (zh) 1991-04-24
KR910006683A (ko) 1991-04-29
EP0417428A3 (en) 1991-11-06
JP3129727B2 (ja) 2001-01-31
AU632607B2 (en) 1993-01-07
BR9004567A (pt) 1991-09-10
DD297697A5 (de) 1992-01-16
AU6025590A (en) 1991-03-14
RU2011942C1 (ru) 1994-04-30
DE59002909D1 (de) 1993-11-04
ATE95303T1 (de) 1993-10-15
US5035283A (en) 1991-07-30
JPH03113295A (ja) 1991-05-14
DE3930205A1 (de) 1991-03-14
CA2024900A1 (fr) 1991-03-10

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