EP0290812A1 - Echangeur de chaleur, particulièrement pour refroidir du gas de crackage - Google Patents

Echangeur de chaleur, particulièrement pour refroidir du gas de crackage Download PDF

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Publication number
EP0290812A1
EP0290812A1 EP88106015A EP88106015A EP0290812A1 EP 0290812 A1 EP0290812 A1 EP 0290812A1 EP 88106015 A EP88106015 A EP 88106015A EP 88106015 A EP88106015 A EP 88106015A EP 0290812 A1 EP0290812 A1 EP 0290812A1
Authority
EP
European Patent Office
Prior art keywords
tube
gas
plate
chamber
plates
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
EP88106015A
Other languages
German (de)
English (en)
Other versions
EP0290812B1 (fr
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
Borsig GmbH
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
Application filed by Borsig GmbH, Deutsche Babcock Borsig AG filed Critical Borsig GmbH
Publication of EP0290812A1 publication Critical patent/EP0290812A1/fr
Application granted granted Critical
Publication of EP0290812B1 publication Critical patent/EP0290812B1/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
    • 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
    • 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
    • F28D7/1607—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 with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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

Definitions

  • the invention relates to a heat exchanger, in particular for cooling cracked gas with the features of the preamble of claim 1 or 2.
  • Such heat exchangers require a construction in which the dividing walls between the heat-dissipating hot cracked gas and the high-pressure heat-absorbing cooling medium are as thin as possible to avoid thermal stresses and to achieve low wall temperatures.
  • a further requirement is the supply of cooling medium, which is sufficient at all times and under all operating conditions, to all surfaces involved in the heat exchange with a simultaneously high flow rate of the cooling medium, in particular to the horizontally arranged exchange surfaces. This high flow rate is necessary to prevent deposits of the particles contained in the cooling medium and thus overheating of the walls.
  • the invention has for its object to simplify the generic heat exchanger in such a way that the smallest possible wall thicknesses with the least possible construction costs are possible.
  • the outer tubes of the double tubes also take on a holding function in addition to the task of flow guidance by anchoring the two tube plates against one another together with the jacket.
  • the tube plates can therefore be made very thin without additional anchors, supporting or holding elements, since the high pressure loads acting on the tube plates are absorbed by the outer tube as a tensile load.
  • the outer tubes have the same wall temperature as the jacket, stresses due to differential expansions due to temperature differences in the jacket, the outer tubes and the tube plates are avoided.
  • a heat exchanger for cooling cracked gas consists of a cylindrical jacket 1, which is provided with an inlet nozzle 2 and an outlet nozzle 3 for a coolant. Boiling water is used as the cooling medium, which is fed into the interior enclosed by the jacket 1 under high pressure.
  • the jacket 1 is provided with a tube plate 4, 5 of small wall thickness.
  • a gas inlet chamber 6 is connected to the tube plates 4, 5 on one side and on the other side a gas outlet chamber 7.
  • the gas inlet chamber 6 is connected to the gas outlet chamber 7 via pipes which extend through the interior of the jacket 1.
  • Each tube is designed as a double tube, which consists of a gas-carrying inner tube 8, which is surrounded by an outer tube 9 to form an annular gap.
  • the inner tube 8 is connected to the outer tube 9 via a fitting 10 which is welded into the tube plate 4 on the side of the outer tube 9.
  • the weld seam is therefore outside of the gas flow which flows into the inner tube 8.
  • the outer tube 9 is provided at various heights with passage openings 11, the last of which is located in the immediate vicinity of the tube plate 5 lying on the gas outlet side.
  • the outer tubes 9 thus serve to guide the cooling medium and to hold the two thin-walled tube plates 4, 5.
  • two separating plates 12, 13 are arranged parallel to the tube plate 4 and are penetrated by the double tubes.
  • the two separating plates 12, 13 delimit with the jacket 1 an inflow chamber 14 into which the inlet connection 2 opens.
  • the second partition plate 13 forms with the tube plate 4 an outflow chamber 15, the volume of which is several times smaller than that of the inflow chamber.
  • the volume ratio can be 1 to 4, for example.
  • the second partition plate 13 is provided with through-flow openings 16, which are each located between the double pipes.
  • the cross section of the throughflow openings 16 is dimensioned so large that a significantly higher speed of the cooling medium results in them than in the inflow chamber 14.
  • the outer tubes 9 and the fittings 10 are provided on the part lying within the outflow chamber 15 with inlet openings 17 through which the cooling medium enters the annular gap of the double tubes.
  • the cooling medium flows out of the annular gap through the passage openings 11 into the interior enclosed by the jacket 1, from which it is discharged via the outlet connection 3.
  • Within the inflow chamber 14 the cooling medium flows from a comparatively large volume at a low flow rate. As it passes through the flow openings 16, the cooling medium experiences an increase in the flow rate.
  • This principle of a low pressure loss due to low flow velocity in the inflow chamber 14 and a subsequently increased pressure loss due to higher flow velocity in the flow openings 16 in the second separating plate 13 ensures that an equal amount of cooling medium flows through all flow openings 16, regardless of whether the Flow opening 16 is located in the vicinity of the inlet nozzle 2, or is removed therefrom. This means that all double pipes are supplied with the same amount of cooling medium.
  • tubular sleeves 18 are inserted, which protrude beyond the second partition plate 13 on both sides.
  • the upwardly projecting edge of the tube sleeves 18 prevents any deposits on the separating plate 13 that are carried along by the cooling medium from being entrained.
  • the lower part of the tube sleeves 18 leads the cooling medium directly to the tube plate 4, from where it flows at high speed along the tube plate 4 to the inlet openings 17 of the double tubes.
  • the cooling medium likewise flows through these inlet openings 17 into the annular gap of the double pipes at high speed.
  • the heat exchanger shown in FIG. 3 has two end chambers 19, 20, one of which is provided with the inlet connection 2 and the other with the outlet connection 3 for the supply and discharge of the coolant.
  • the end chambers 19, 20 are connected by the double tubes formed from gas-carrying inner tube 8 and outer tube 9 and adjoin the gas inlet chamber 6 or the gas outlet chamber 7.
  • Each end chamber 19, 20 contains on the gas side one of the described tube plates 4, 5, which are connected via a side wall 21 to a second plate 22.
  • the outer tubes 9 are welded into these plates 4, 5, 22, so that the plates are anchored to one another via the outer tubes 9.
  • the outer tubes 9 are provided with inlet openings 17 and outlet openings 23 on the part lying within the end chambers 19, 20.
  • the end chamber 19 lying on the gas inlet side is divided into an inflow chamber 14 of larger volume and an inflow chamber 15 of smaller volume by a partition plate 13 provided with throughflow openings 16.
  • An overflow weir 24 is connected to the separating plate 13 and stands on the tube plate 4.
  • the cooling medium fed through the inlet nozzle 2 into the end chamber 19 enters the inflow chamber 14 via the overflow weir 24, reaches the outflow chamber 15 with increasing flow velocity, through the inlet openings 17 into the annular space of the double pipes and through the outlet openings 23 into the other end chamber 21, from where it is discharged through the outlet nozzle 3.

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)
EP88106015A 1987-05-12 1988-04-15 Echangeur de chaleur, particulièrement pour refroidir du gas de crackage Expired - Lifetime EP0290812B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3715712A DE3715712C1 (de) 1987-05-12 1987-05-12 Waermetauscher insbesondere zum Kuehlen von Spaltgas
DE3715712 1987-05-12

Publications (2)

Publication Number Publication Date
EP0290812A1 true EP0290812A1 (fr) 1988-11-17
EP0290812B1 EP0290812B1 (fr) 1991-01-02

Family

ID=6327297

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88106015A Expired - Lifetime EP0290812B1 (fr) 1987-05-12 1988-04-15 Echangeur de chaleur, particulièrement pour refroidir du gas de crackage

Country Status (4)

Country Link
US (1) US4848449A (fr)
EP (1) EP0290812B1 (fr)
JP (1) JP2722076B2 (fr)
DE (2) DE3715712C1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005116560A1 (fr) * 2004-05-25 2005-12-08 Shell Internationale Research Maatschappij B.V. Appareil de refroidissement d'un gaz chaud
EP3032209A1 (fr) * 2014-12-11 2016-06-15 Borsig GmbH Systeme de refroidisseur a injection
EP3899396B1 (fr) 2018-12-20 2022-09-14 Hexsol Italy Srl Echangeur de chaleur comportant une jonction d'extremite

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3822808C2 (de) * 1988-07-06 1993-12-23 Balcke Duerr Ag Wärmetauscher mit zwischen zwei Rohrplatten angeordneten Wärmetauscherrohren
DE3908277C2 (de) * 1989-03-14 1995-11-30 Oemv Deutschland Gmbh Erosionsschutz für Wärmetauscher
DE3930205A1 (de) * 1989-09-09 1991-03-14 Borsig Babcock Ag Rohrbuendel-waermetauscher
US5425415A (en) * 1993-06-15 1995-06-20 Abb Lummus Crest Inc. Vertical heat exchanger
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
DE19501422C2 (de) * 1995-01-19 2002-03-28 Borsig Gmbh Gekühltes Übergangsstück zwischen einem Wärmetauscher und einem Reaktor
DE19546002C2 (de) * 1995-12-09 1998-06-04 Renzmann Und Gruenewald Gmbh Doppelrohrwärmetauscher
US5813453A (en) * 1996-06-01 1998-09-29 Deutsche Babcock-Borsig Ag Heat exchanger for cooling cracked gas
US6772830B1 (en) * 1999-07-21 2004-08-10 Stone & Webster, Inc. Enhanced crossflow heat transfer
KR101227444B1 (ko) * 2004-05-25 2013-01-29 쉘 인터내셔날 리써취 마트샤피지 비.브이. 고온 가스의 냉각 장치
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
US10196088B2 (en) 2011-04-19 2019-02-05 Ford Global Technologies, Llc Target monitoring system and method
US9937953B2 (en) 2011-04-19 2018-04-10 Ford Global Technologies, Llc Trailer backup offset determination
US9963004B2 (en) 2014-07-28 2018-05-08 Ford Global Technologies, Llc Trailer sway warning system and method
US10384607B2 (en) 2015-10-19 2019-08-20 Ford Global Technologies, Llc Trailer backup assist system with hitch angle offset estimation
US10611407B2 (en) 2015-10-19 2020-04-07 Ford Global Technologies, Llc Speed control for motor vehicles
US9836060B2 (en) 2015-10-28 2017-12-05 Ford Global Technologies, Llc Trailer backup assist system with target management
US10017115B2 (en) 2015-11-11 2018-07-10 Ford Global Technologies, Llc Trailer monitoring system and method
US10155478B2 (en) 2015-12-17 2018-12-18 Ford Global Technologies, Llc Centerline method for trailer hitch angle detection
US10011228B2 (en) 2015-12-17 2018-07-03 Ford Global Technologies, Llc Hitch angle detection for trailer backup assist system using multiple imaging devices
US9934572B2 (en) 2015-12-17 2018-04-03 Ford Global Technologies, Llc Drawbar scan solution for locating trailer hitch point
US9827818B2 (en) 2015-12-17 2017-11-28 Ford Global Technologies, Llc Multi-stage solution for trailer hitch angle initialization
US10005492B2 (en) 2016-02-18 2018-06-26 Ford Global Technologies, Llc Trailer length and hitch angle bias estimation
US10106193B2 (en) 2016-07-01 2018-10-23 Ford Global Technologies, Llc Enhanced yaw rate trailer angle detection initialization
US10046800B2 (en) 2016-08-10 2018-08-14 Ford Global Technologies, Llc Trailer wheel targetless trailer angle detection
CN106197126B (zh) * 2016-08-31 2019-03-15 浙江格尔泰斯环保特材科技股份有限公司 一种管式气气换热器的顶板
CN106197127B (zh) * 2016-08-31 2019-06-07 浙江格尔泰斯环保特材科技股份有限公司 一种管式气气换热器的底板
US10222804B2 (en) 2016-10-21 2019-03-05 Ford Global Technologies, Llc Inertial reference for TBA speed limiting
US10710585B2 (en) 2017-09-01 2020-07-14 Ford Global Technologies, Llc Trailer backup assist system with predictive hitch angle functionality
CN108362155A (zh) * 2018-02-08 2018-08-03 王萍 一种基于热交换技术的工业废气热能二次利用装置
US11077795B2 (en) 2018-11-26 2021-08-03 Ford Global Technologies, Llc Trailer angle detection using end-to-end learning
US10829046B2 (en) 2019-03-06 2020-11-10 Ford Global Technologies, Llc Trailer angle detection using end-to-end learning

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR603110A (fr) * 1925-08-12 1926-04-09 Appareil à tubes concentriques pour l'échange de chaleur entre fluides
US1782435A (en) * 1926-11-09 1930-11-25 Gen Chemical Corp Apparatus for cooling fluids
GB969036A (en) * 1960-09-21 1964-09-09 Fives Penhoet Improvements in or relating to tubular heat exchange apparatus
DE1805264A1 (de) * 1967-10-27 1969-05-22 Rosenlew Ab Oy W Waermeaustauscher
DE1551480B1 (de) * 1967-01-05 1971-03-11 Mannesmann Ag Doppelrohr waermetauscher fuer hohe druecke
GB2057666A (en) * 1979-07-30 1981-04-01 Toyo Engineering Corp Heat exchangers
DE3310375A1 (de) * 1983-03-22 1984-09-27 Franz 7505 Ettlingen Gärtner Waermetauscher

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FR1161500A (fr) * 1956-09-28 1958-09-01 Stein & Roubaix échangeur thermique à faisceaux tubulairees multiples
US3117559A (en) * 1960-09-21 1964-01-14 Fives Penhoet Heat exchanger
AT339636B (de) * 1971-11-26 1977-10-25 Messer Griesheim Gmbh Vorrichtung zur kuhlung von flussigen kraftstoffen oder ahnlichen flussigkeiten
US4585057A (en) * 1982-09-30 1986-04-29 Krw Energy Systems Inc. Cooled tubesheet inlet for abrasive fluid heat exchanger
US4570702A (en) * 1983-03-28 1986-02-18 Chicago Bridge & Iron Company Shell and tube vertical heat exchanger with sleeves around the tubes
JPS6042843A (ja) * 1983-08-18 1985-03-07 Rohm Co Ltd 半導体ウェファ
DE3411795A1 (de) * 1984-03-30 1985-10-03 Borsig Gmbh, 1000 Berlin Verfahren zum betreiben von rohrbuendelwaermeaustauschern zum kuehlen von gasen
DE3533219C1 (de) * 1985-09-18 1986-11-13 Borsig Gmbh, 1000 Berlin Rohrbuendelwaermetauscher
FR2599133B1 (fr) * 1986-05-21 1990-09-21 Struthers Wells Sa Echangeur de chaleur tubulaire a double plaque de support du faisceau de tube

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR603110A (fr) * 1925-08-12 1926-04-09 Appareil à tubes concentriques pour l'échange de chaleur entre fluides
US1782435A (en) * 1926-11-09 1930-11-25 Gen Chemical Corp Apparatus for cooling fluids
GB969036A (en) * 1960-09-21 1964-09-09 Fives Penhoet Improvements in or relating to tubular heat exchange apparatus
DE1551480B1 (de) * 1967-01-05 1971-03-11 Mannesmann Ag Doppelrohr waermetauscher fuer hohe druecke
DE1805264A1 (de) * 1967-10-27 1969-05-22 Rosenlew Ab Oy W Waermeaustauscher
GB2057666A (en) * 1979-07-30 1981-04-01 Toyo Engineering Corp Heat exchangers
DE3310375A1 (de) * 1983-03-22 1984-09-27 Franz 7505 Ettlingen Gärtner Waermetauscher

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005116560A1 (fr) * 2004-05-25 2005-12-08 Shell Internationale Research Maatschappij B.V. Appareil de refroidissement d'un gaz chaud
CN101389920B (zh) * 2004-05-25 2010-11-03 国际壳牌研究有限公司 用于冷却热气体的设备
US8186423B2 (en) 2004-05-25 2012-05-29 Shell Oil Company Apparatus for cooling a hot gas
EP3032209A1 (fr) * 2014-12-11 2016-06-15 Borsig GmbH Systeme de refroidisseur a injection
CN105698572A (zh) * 2014-12-11 2016-06-22 波尔希克有限公司 淬火冷却系统
CN105698572B (zh) * 2014-12-11 2019-03-08 波尔希克有限公司 淬火冷却系统
EP3899396B1 (fr) 2018-12-20 2022-09-14 Hexsol Italy Srl Echangeur de chaleur comportant une jonction d'extremite
US11656031B2 (en) 2018-12-20 2023-05-23 Hexsol Italy Srl Junctions for double-walled tubes in heat exchangers and exchangers with such junctions

Also Published As

Publication number Publication date
JP2722076B2 (ja) 1998-03-04
DE3861347D1 (de) 1991-02-07
JPS63297994A (ja) 1988-12-05
US4848449A (en) 1989-07-18
EP0290812B1 (fr) 1991-01-02
DE3715712C1 (de) 1988-07-21

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