EP0436828A2 - Echangeur de chaleur pour le refroidissement de gaz de réaction chauds - Google Patents

Echangeur de chaleur pour le refroidissement de gaz de réaction chauds Download PDF

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Publication number
EP0436828A2
EP0436828A2 EP90123071A EP90123071A EP0436828A2 EP 0436828 A2 EP0436828 A2 EP 0436828A2 EP 90123071 A EP90123071 A EP 90123071A EP 90123071 A EP90123071 A EP 90123071A EP 0436828 A2 EP0436828 A2 EP 0436828A2
Authority
EP
European Patent Office
Prior art keywords
gas
cooling
heat exchanger
tube plate
cooling 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.)
Granted
Application number
EP90123071A
Other languages
German (de)
English (en)
Other versions
EP0436828B1 (fr
EP0436828A3 (en
Inventor
Peter Brücher
Wolfgang Kehrer
Dieter Bormann
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
Application filed by Deutsche Babcock Borsig AG filed Critical Deutsche Babcock Borsig AG
Priority to AT90123071T priority Critical patent/ATE99409T1/de
Publication of EP0436828A2 publication Critical patent/EP0436828A2/fr
Publication of EP0436828A3 publication Critical patent/EP0436828A3/de
Application granted granted Critical
Publication of EP0436828B1 publication Critical patent/EP0436828B1/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
    • F28D7/005—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 for only one medium being tubes having bent portions or being assembled from bent tubes or being tubes having a toroidal configuration
    • 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 heat exchanger for cooling hot reaction gas with the aid of a cooling medium with the features of the preamble of patent claim 1.
  • a known heat exchanger (DE-PS 28 18 892) contains a tube plate which consists of a thick tube sheet, which is penetrated by the gas-carrying tubes with the formation of annular gaps, and consists of a thin tube sheet into which the gas-carrying tubes are welded.
  • the thin tube sheet is connected on the outer circumference to the thick tube sheet and is supported on it by the gas-carrying tubes.
  • a supply line for the cooling medium opens into the space between the two tube sheets and enters the interior of the heat exchanger through the annular gaps.
  • the known heat exchanger has the disadvantage that particles contained in the water serving as a cooling medium are deposited on the inside of the thin tube sheet and there can lead to overheating.
  • a standing heat exchanger with a tube bundle held in two tube plates is known (AT-PS 361 953), in which the upper tube plate arranged on the gas outlet side also
  • Cooling channels is provided. These cooling channels are connected to the interior of the heat exchanger via the annular gaps surrounding the gas-carrying pipes.
  • the invention has for its object to design the generic heat exchanger such that the tube plate on the gas side has a small wall thickness and that the cooling medium is passed through the tube plate so that no solid particles from the cooling medium can deposit on the cooling medium side of the tube plate.
  • the tube plate of the heat exchanger according to the invention can be made thick overall and thus meet the requirement to withstand the high pressure of the cooling medium.
  • the wall thickness between the heat-emitting hot reaction gas and the high-pressure heat-absorbing boiling water serving as the cooling medium can be kept low. In this way, thermal stresses can be reduced and low wall temperatures can be achieved in the tube plate.
  • the cooling medium can be guided in the cooling channels in such a manner and at such a speed that the solid particles contained in the cooling medium cannot be deposited on the cooling medium side of the tube plate, but instead are washed away. Since the tube plate is higher than the lower edge of the surrounding jacket, the solid particles can collect below the tube plate in the lowest point of the heat exchanger.
  • the heat exchanger is of a standing type and consists of a jacket 1, which is closed at the top by a dome 2 and is provided with a flange 3 on its lower edge.
  • the heat exchanger stands on a gas supply chamber 4, the jacket of which is provided on the inside with a refractory lining 5.
  • a pressure-operated reactor (not shown), which can belong to an oil gasification plant.
  • the jacket 1 of the heat exchanger is separated from the gas supply chamber 4 by a tube plate 6.
  • the tube plate 6 has a smaller diameter than the jacket 1.
  • Via an inwardly facing cone 7, the tube plate 6 is connected to the flange 3, which represents the lower edge of the jacket 1, in such a way that the tube plate 6 lies above the flange 3.
  • the cone 7, like the gas supply chamber, is provided with a fireproof covering 5.
  • the tube plate 6 is provided in the longitudinal direction of the heat exchanger with tube bores 8 through which tubes 9 are passed. There is an annular gap 10 between each tube 9 and the associated tube bore 8. The inlet ends of the tubes 9 are tightly welded into the tube plate 6 on the side against which the gas flows from the gas supply chamber 4.
  • each tube 9 is bent into a tube spiral, the end of which is connected to a connecting piece 11 which is guided through the jacket 1 just above the tube plate 6.
  • the gas from the gas supply chamber 4 flows through the tubes 9 and is thereby cooled by a cooling medium which is fed in the manner described later through a plurality of supply lines 12 into the interior 13 of the heat exchanger enclosed by the jacket 1.
  • Pressurized water serves as the cooling medium, which evaporates through the heat exchange with the hot gas and leaves the heat exchanger as steam via an outlet connection 14 in the dome 3.
  • the tube plate 6 is provided in the half facing the gas inlet with parallel cooling channels 15, which are open to the interior 13 of the heat exchanger.
  • the width of the cooling channels 15 is selected so that the cooling channels 15 cut the pipe bores 8.
  • the cooling channels 15 are preferably closed on one side by a cover 16 connected to the outer circumference of the tube plate 9. Adjacent cooling channels 15 can be closed at opposite ends.
  • Each cooling channel 15 is provided in the vicinity of the closed end with one of the supply lines 12 for the cooling medium. 2, the feed line 12 is guided from above through the tube plate 6 into the cooling channel 15 in question.
  • the cooling medium can also be fed laterally into the cooling channels 15. If adjacent cooling channels 15 are closed at opposite ends, this results in opposing flows of the cooling medium in adjacent cooling channels 15.
  • the cooling medium penetrates into the annular gaps 10 and generates a rotary flow around the tubes 9, which results in intensive cooling of these hot parts.
  • the water fed through the supply lines 12 enters the cooling channels 15, flows through them, partly rises through the annular gaps 10 and enters the interior 13 of the heat exchanger.
  • the remaining part of the cooling medium flows through the open ends of the cooling channels 15 directly into the interior 13.
  • Solid particles that are still contained in the cooling medium despite careful preparation are flushed out of the cooling channels 15 with the cooling medium stream and settle in the lowest point of the heat exchanger from.
  • This lowest point lies below the tube plate 6 in the annular space between the cone 7 and the jacket 1.
  • This annular space is unheated since the cone 7 is provided with the refractory lining 5 on the gas side.
  • a suction line 17 opens into the annular space, via which the deposited solid particles can be removed from the heat exchanger.
  • the tube plate 6 has emergency cooling properties in the event of a failure of the cooling medium supply and a subsequent interruption of the gas supply. In this case, the stored heat is still to be dissipated, which is done in that cooling medium is drawn in from the interior 13 through the cooling channels 15. This cooling medium flow ensures cooling of the tube plate 6.
  • cooling bores 18, which are open on both sides, can be passed through the tube plate 6 near the side exposed to the gas parallel to the cooling channels 15.
  • These cooling holes 18 have a smaller cross section than the cooling channels 15.
  • the internal cooling holes 18 open into the annular gaps 10.
  • the cooling channels 15 can also be divided into two superposed partial channels 20, 21 by a partition plate 19.
  • each sub-channel 20, 21 be provided with its own cooling medium connection.
  • the inner tube 22 carries colder cooling medium, for. B. fresh water, in the lower sub-channel 20, while the upper sub-channel 21 with warmer cooling medium, for. B. circulating water, is fed from the annular space between the inner tube 22 and the jacket of the feed line 12.

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)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Devices And Processes Conducted In The Presence Of Fluids And Solid Particles (AREA)
  • Details Of Measuring And Other Instruments (AREA)
EP90123071A 1990-01-10 1990-12-03 Echangeur de chaleur pour le refroidissement de gaz de réaction chauds Expired - Lifetime EP0436828B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90123071T ATE99409T1 (de) 1990-01-10 1990-12-03 Waermetauscher zum kuehlen von heissem reaktionsgas.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4000527A DE4000527A1 (de) 1990-01-10 1990-01-10 Waermetauscher zum kuehlen von heissem reaktionsgas
DE4000527 1990-01-10

Publications (3)

Publication Number Publication Date
EP0436828A2 true EP0436828A2 (fr) 1991-07-17
EP0436828A3 EP0436828A3 (en) 1991-11-27
EP0436828B1 EP0436828B1 (fr) 1993-12-29

Family

ID=6397827

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90123071A Expired - Lifetime EP0436828B1 (fr) 1990-01-10 1990-12-03 Echangeur de chaleur pour le refroidissement de gaz de réaction chauds

Country Status (5)

Country Link
US (1) US5088551A (fr)
EP (1) EP0436828B1 (fr)
JP (1) JPH06201290A (fr)
AT (1) ATE99409T1 (fr)
DE (2) DE4000527A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4407594A1 (de) * 1994-03-08 1995-09-14 Borsig Babcock Ag Wärmetauscher zum Kühlen von heißem Reaktionsgas
DE4445687A1 (de) * 1994-12-21 1996-06-27 Borsig Babcock Ag Wärmetauscher zum Kühlen von Spaltgas
US5775412A (en) * 1996-01-11 1998-07-07 Gidding Engineering, Inc. High pressure dense heat transfer area heat exchanger
US5813453A (en) * 1996-06-01 1998-09-29 Deutsche Babcock-Borsig Ag Heat exchanger for cooling cracked gas
DE29610883U1 (de) * 1996-06-21 1997-10-16 Engelhardt, Wolfgang, Dipl.-Ing., 40545 Düsseldorf Wärmetauscher
DE19833004A1 (de) * 1998-07-22 2000-01-27 Borsig Gmbh Wärmetauscher zum Kühlen eines heißen Prozeßgases
IT1403894B1 (it) * 2010-12-29 2013-11-08 Eni Spa Scambiatore di calore per il raffreddamento di gas caldi e sistema di scambio termico

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1129588A (en) * 1964-12-24 1968-10-09 Schmidt Sche Heissdampf Improvements relating to heat exchangers for cooling freshly cracked gases
US3477495A (en) * 1966-05-13 1969-11-11 Lummus Co Inlet cone device and method
DE1953628A1 (de) * 1969-10-24 1971-05-06 Steinmueller Gmbh L & C Rohrbuendel-Waermeaustauscher

Family Cites Families (9)

* 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
US4117885A (en) * 1974-09-30 1978-10-03 Foster Wheeler Limited Slab header
GB1488349A (en) * 1974-11-29 1977-10-12 Haldor Topsoe As Heat exchange apparatus
DE2642800C2 (de) * 1976-09-23 1982-12-09 Deggendorfer Werft Und Eisenbau Gmbh, 8360 Deggendorf Rohrbodenanschluß für Rohrbündel-Reaktoren oder Rohrbündel-Wärmeaustauscher
US4157114A (en) * 1977-08-22 1979-06-05 Lorenzo John F De Tubesheet with a thermal sleeve
US4202406A (en) * 1978-06-29 1980-05-13 Avery Alfred J Heat exchange system
NL7905640A (nl) * 1978-09-14 1980-03-18 Borsig Gmbh Van een pijpenbundel voorziene warmtewisselaar.
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−
US4488513A (en) * 1983-08-29 1984-12-18 Texaco Development Corp. Gas cooler for production of superheated steam

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1129588A (en) * 1964-12-24 1968-10-09 Schmidt Sche Heissdampf Improvements relating to heat exchangers for cooling freshly cracked gases
US3477495A (en) * 1966-05-13 1969-11-11 Lummus Co Inlet cone device and method
DE1953628A1 (de) * 1969-10-24 1971-05-06 Steinmueller Gmbh L & C Rohrbuendel-Waermeaustauscher

Also Published As

Publication number Publication date
EP0436828B1 (fr) 1993-12-29
JPH06201290A (ja) 1994-07-19
US5088551A (en) 1992-02-18
EP0436828A3 (en) 1991-11-27
ATE99409T1 (de) 1994-01-15
DE4000527A1 (de) 1991-07-11
DE59004035D1 (de) 1994-02-10

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