EP0094097A2 - Plaque tubulaire, pas bouchante, à pression égalisée pour échangeur de chaleur à gazéification - Google Patents

Plaque tubulaire, pas bouchante, à pression égalisée pour échangeur de chaleur à gazéification Download PDF

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Publication number
EP0094097A2
EP0094097A2 EP83104681A EP83104681A EP0094097A2 EP 0094097 A2 EP0094097 A2 EP 0094097A2 EP 83104681 A EP83104681 A EP 83104681A EP 83104681 A EP83104681 A EP 83104681A EP 0094097 A2 EP0094097 A2 EP 0094097A2
Authority
EP
European Patent Office
Prior art keywords
tube sheet
chamber
heat exchanger
inlet
shell
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Withdrawn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
EP83104681A
Other languages
German (de)
English (en)
Other versions
EP0094097A3 (fr
Inventor
John Anthony Rylatt
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.)
KRW Energy Systems Inc
Original Assignee
KRW Energy Systems Inc
Westinghouse Electric Corp
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 KRW Energy Systems Inc, Westinghouse Electric Corp filed Critical KRW Energy Systems Inc
Publication of EP0094097A2 publication Critical patent/EP0094097A2/fr
Publication of EP0094097A3 publication Critical patent/EP0094097A3/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Withdrawn legal-status Critical Current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
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • 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
    • F28D3/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium flows in a continuous film, or trickles freely, over the conduits
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10J—PRODUCTION OF PRODUCER GAS, WATER-GAS, SYNTHESIS GAS FROM SOLID CARBONACEOUS MATERIAL, OR MIXTURES CONTAINING THESE GASES; CARBURETTING AIR OR OTHER GASES
    • C10J3/00—Production of combustible gases containing carbon monoxide from solid carbonaceous fuels
    • C10J3/46—Gasification of granular or pulverulent flues in suspension
    • C10J3/48—Apparatus; Plants
    • C10J3/485—Entrained flow gasifiers
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10J—PRODUCTION OF PRODUCER GAS, WATER-GAS, SYNTHESIS GAS FROM SOLID CARBONACEOUS MATERIAL, OR MIXTURES CONTAINING THESE GASES; CARBURETTING AIR OR OTHER GASES
    • C10J3/00—Production of combustible gases containing carbon monoxide from solid carbonaceous fuels
    • C10J3/72—Other features
    • C10J3/723—Controlling or regulating the gasification process
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10J—PRODUCTION OF PRODUCER GAS, WATER-GAS, SYNTHESIS GAS FROM SOLID CARBONACEOUS MATERIAL, OR MIXTURES CONTAINING THESE GASES; CARBURETTING AIR OR OTHER GASES
    • C10J3/00—Production of combustible gases containing carbon monoxide from solid carbonaceous fuels
    • C10J3/72—Other features
    • C10J3/86—Other features combined with waste-heat boilers
    • 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
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10J—PRODUCTION OF PRODUCER GAS, WATER-GAS, SYNTHESIS GAS FROM SOLID CARBONACEOUS MATERIAL, OR MIXTURES CONTAINING THESE GASES; CARBURETTING AIR OR OTHER GASES
    • C10J2300/00—Details of gasification processes
    • C10J2300/18—Details of the gasification process, e.g. loops, autothermal operation
    • C10J2300/1861—Heat exchange between at least two process streams
    • C10J2300/1892—Heat exchange between at least two process streams with one stream being water/steam

Definitions

  • This invention relates to gasification of carbonaceous materials, and more particularly to apparatus for cooling the raw gas from fluidized bed gasification reactors.
  • a combustible product gas is produced, as well as solid waste products such as agglomerated ash.
  • PDU Process Development Unit
  • particulate coal is injected through one of a number of concentric tubes extending upwardly into the center of a vertical bed-containing pressure vessel. Fluidization occurs in the upper sections.
  • the untreated product gas from gasified coal is called raw gas and contains a significant amount of particles which are molten at the gasifier exit temperatures of approximately 980°C. These particles, which are of varying chemical composition, will stick both to metallic and non-metallic surfaces regardless of the angle of incidence of the gas flow to the surface, as the gas flows from the gasifier exit. It has been demonstrated that eventually the flow passages plug almost closed with solidified material.
  • Condition (a) has been achieved by water spray quench, but is not energy efficient for certain operations.
  • Condition (b) has been achieved by water cooling of an uninsulated metal plate, but erosion has been significant and the pressure differential across the plate necessitates compliance with ASME Boiler and Pressure Vessel Code Section VIII.
  • the present invention resides in a heat exchanger for a gas carrying an abrasive particulate
  • a heat exchanger for a gas carrying an abrasive particulate comprising a shell having first and second tube sheets extending thereacross at opposite ends thereof and defining particulate containing fluid inlet and outlet chambers, a plurality of tubes supported within said shell between said tube sheets, a third tube sheet extending across said shell adjacent to but spaced from said first tube sheet so as to divide the space between said first and second tube sheets into a first chamber adjacent the inlet end and a second chamber adjacent the outlet end of said shell, inlet means associated with said inlet chamber for admitting said particulate.containing fluid into said inlet chamber, said inlet chamber being in flow communication with the outlet chamber through said tubes, means for flowing a cooling fluid through said second chamber in heat exchange relation with said particulate containing fluid, and means for conducting a buffer fluid through said first chamber, characterized by a pressure equalizing means between said inlet and said first chambers adapted to reduce pressure
  • the raw gas which contains entrained particles from gasified material acting as a severe abrasive directly is cooled by a liquid cooling system at the same pressure as the raw gas, using a pressure equalizing system comprising a surge tank to allow pressure transmittal without movement of one fluid into the system of the other fluid.
  • a pressure equalizing system comprising a surge tank to allow pressure transmittal without movement of one fluid into the system of the other fluid.
  • a cooled tube sheet heat exchanger 10 in accordance with the state of the art, comprising a shell 12 containing an inlet port 14, an upper tube sheet 16, a middle tube sheet 18, a lower tube sheet 20, and tubes 22 disposed through the tube sheets 16, 18 and 20, and an outlet port 24.
  • Penetrating the shell 12 between tube sheets 18 and 20 are an inlet opening 26 and an outlet opening 28 through which flows a first fluid medium in heat exchange relation with tubes 22.
  • Penetrating the shell 12 between tube sheets 16 and 18 are an inlet orifice 30 and an outlet orifice 32 of a tube sheet cooling system 34 using a second fluid medium and comprising piping 36, an auxiliary heat exchanger 38 and a pump 40.
  • a third fluid medium containing an abrasive material such as raw gas from a coal gasification system, containing entrained particles from gasified coal, enters the shell 12 at the inlet port 14.
  • the particles impinge on the upper tube sheet 16, gradually eroding away the upper tube sheet 16.
  • the raw gas and particles then flow through the tubes 22, and out through the outlet port 24 of the heat exchanger 10.
  • the first fluid medium flows through the inlet opening 26, cools the tubes 22 and flows out the outlet opening 28.
  • the tube sheet cooling system 34 operates in the following manner.
  • a second fluid medium is moved by pump 40 through inlet orifice 30 between the upper tube sheet 16 and the middle tube sheet 18, cooling the upper tube sheet 16, thence through outlet orifice 32, through piping 36 and the auxiliary heat exchanger 38.
  • the tube sheet cooling system 34 helps to reduce deposition of the entrained particles on the upper tube sheet 16.
  • the upper tube sheet 16 must be built to withstand pressure differentials of greater than 15 psi, thereby necessitating a thicker upper tube sheet 16 and compliance with ASME Code requirements.
  • a cooled, pressure equalized tube sheet heat exchanger 50 in accordance with the invention comprising a shell 52 containing an inlet port 54, an upper tube sheet 56, a middle tube sheet 58, a lower tube sheet 60, tubes 62 disposed through the upper, middle and lower tube sheets 56, 58 and 60 respectively, and outlet port 64.
  • Penetrating the shell 52 between tube sheets 58 and 60 are an inlet opening 66 and an outlet opening 68 through which flows a first fluid medium in heat exchange relation with tubes 62.
  • Penetrating the shell 52 between tube sheets 56 and 58 are an inlet orifice 70 and an outlet orifice 72 of a tube sheet cooling system 74 using a second fluid medium typically water, and comprising piping 76, an auxiliary heat exchanger 78 and a pump 80.
  • a second fluid medium typically water
  • a pressure equalizing system 82 comprising a surge tank 84 and pressure conduit 86 is connected to the heat exchanger 50 by a shell hole 88 and tube sheet cooling system hole 90.
  • a third fluid medium containing an abrasive material such as raw gas from a coal gasification system, containing entrained particles from gasified coal, enters the shell 52 at the inlet port 54.
  • the particles impinge on the upper tube sheet 56, gradually eroding away the upper tube sheet 56.
  • the raw gas and particles then flow through the tubes 62, and out the outlet port 64 of the heat exchanger 50.
  • the tube sheet cooling system 74 operates in the following manner.
  • a second fluid medium is moved by pump 80 between the upper tube sheet 56 and the middle tube sheet 58, cooling the upper tube sheet 56, thence through piping 76 and the auxiliary heat exchanger 78.
  • the pressure equalizing system 82 operates by transmitting the pressure of the raw gas through shell hole 88, and pressure conduit 86, into the surge tank 84.
  • the surge tank 84 transmits the pressure through the pressure conduit 86 and the tube sheet cooling system hole 90 into the tube sheet cooling system 74.
  • the upper tube sheet 56 When it has been determined that the upper tube sheet 56 has outlived its usefulness due to erosion, the the upper tube sheet 56 is removed, and new upper tube sheet 56 is installed in its place. Since the pressure between the raw gas and the tube sheet cooling system 74 is now equalized by the pressure equalizing system 82, the upper tube sheet 56 will not be exposed to pressure differentials of greater than about lkg/cm 2 , the upper tube sheet 56 may be thinner, and the ASME Code requirements need not be met.
  • a cooled, pressure- equalized, removable tube sheet heat exchanger 101 in accordance with the invention comprising a shell 103 having an upper section 105, a middle section 107, and a lower section 109.
  • the upper section 105 and the middle section 107 are mated at an upper flange 111
  • the middle section 107 and the lower section 109 are mated at a lower flange 113.
  • the flanges 111 and 113 will typically be mated by bolts 114, but any fastening means is acceptable.
  • the upper section 105 is comprised of an inlet port 115.
  • the middle section 107 is comprised of a middle section upper tube sheet 117, a middle section lower tube sheet 119, and a first set of tubes 121 disposed through the middle section upper tube sheet 117 and the middle section lower tube sheet 119.
  • the lower section 109 is comprised of a lower section upper tube sheet 123, a lower section lower tube sheet 125, a second set of tubes 127 disposed through the lower section upper tube sheet 123 and the lower section lower tube sheet 125, and an outlet port 129 below the lower section lower tube sheet 125.
  • first cavity 131 above the middle section upper tube sheet 117
  • second cavity 133 between the middle section upper tube sheet 117 and the middle section lower tube sheet 119
  • third cavity 135 between the middle section lower tube sheet 119 and the lower section upper tube sheet 123
  • fourth cavity 137 between the lower section upper tube sheet 123 and the lower section lower tube sheet 125
  • fifth cavity 139 below the lower section lower tube sheet 125.
  • the first set of tubes 121 is in flow communication with the first cavity 131 and the third cavity 135, and the second set of tubes 127 is in flow communication with the third cavity 135 and the fifth cavity 139.
  • the first set of tubes 121 will typically abut the second set of tubes 127 within the third cavity 135.
  • the lower section 109 further comprises inlet opening 141 and outlet opening 143 in the shell 103 in flow communication with the fourth cavity 137.
  • the heat exchanger 101 further comprises a tube sheet cooling system 145 which is attached to the heat exchanger 101 in the middle section 107 at inlet orifice 147 and outlet orifice 149 and in flow communication with the second cavity 133.
  • the tube sheet cooling system 145 comprises piping 151, an auxiliary heat exchanger 153, a pump 155, and a pressure equalizing flask 157.
  • the pressure equalizing flask 157 is connected to the piping 151 and the shell 103. Thus the pressure equalizing flask 157 is in flow communication with the tube sheet cooling system 145 and the first cavity 131.
  • a first fluid medium containing an abrasive material such as raw gas from a carbonaceous material gasification system, containing entrained particles from gasified coal enters the shell 103 at the inlet port 115.
  • the particles impinge on the middle section upper tube sheet 117 gradually eroding away the middle section upper tube sheet 117.
  • the raw gas and particles then flow through the first set of tubes 121, into and through the second set of tubes 127 and into the fifth cavity 139 thence out of the heat exchanger 101 through outlet port 129.
  • a second fluid medium typically water, enters the fourth cavity 137 through inlet opening 141, exits through outlet opening 143, and is in heat exchange relation with the second set of tubes 127.
  • the tube sheet cooling system 145 operates in the following manner.
  • a third fluid medium typically water
  • Pressure across the middle section upper tube sheet 117 is equalized by the transmittal of pressure through the pressure equalizing flask 157 which is in flow communication with the first cavity 131 and the tube sheet cooling system 145.
  • there will be a gas/liquid interface within the pressure equalizing flask 157 which will minimize mixing between the first and third fluid mediums.
  • the third fluid medium could be a gas. This embodiment would also result in a gas/liquid interface.
  • the middle section 107 When it has been determined that the middle section upper tube sheet 117 has outlived its usefulness due to erosion, the middle section 107 will be separated from the heat exchanger 101 at flanges 111 and 113 and an identical new middle section 107 comprising middle section upper tube sheet 117, middle section lower tube sheet 119 and first set of tubes 121 is installed in its place. Since the pressure in the first cavity 131 is equalized with 1) the pressure in the second cavity 133 through the pressure equalizing flask 157, and 2) the pressure in the third cavity 135 through the first set of tubes 121, it can be seen that the pressure differentials across the middle section upper tube sheet 117 and middle section lower tube sheet 119 are all less than 15 psi.
  • the preferred embodiment of the invention has several advantages over the prior art.
  • One advantage is that, in an abrasive environment which causes severe erosion of the tube sheet, an easily replaceable tube sheet will save a significant portion of the cost of the entire heat exchanger 101 and reduce down time. This results from the ability to repair a heat exchanger 1) using a component cheaper than the whole heat exchanger, 2) faster than the replacement of the whole heat exchanger.
  • Another advantage is that, since the pressure differential across the tube sheets 117 and 119 contained in the removable middle section 107 is less than 15 psi, the requirements of ASME Boiler and Pressure Code Section VIII are not applicable. As a result, the tube sheets 117 and 119 can be made thinner and without the stringent quality controls of the ASME Code.
  • a further advantage of the invention is that due to the cooled tube sheet feature, the heat exchanger 101 will be less likely to plug and will therefore require less maintenance and repair.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Organic Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Industrial Gases (AREA)
EP83104681A 1982-05-11 1983-05-11 Plaque tubulaire, pas bouchante, à pression égalisée pour échangeur de chaleur à gazéification Withdrawn EP0094097A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US37723082A 1982-05-11 1982-05-11
US377230 1982-05-11

Publications (2)

Publication Number Publication Date
EP0094097A2 true EP0094097A2 (fr) 1983-11-16
EP0094097A3 EP0094097A3 (fr) 1984-05-09

Family

ID=23488269

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83104681A Withdrawn EP0094097A3 (fr) 1982-05-11 1983-05-11 Plaque tubulaire, pas bouchante, à pression égalisée pour échangeur de chaleur à gazéification

Country Status (7)

Country Link
EP (1) EP0094097A3 (fr)
JP (1) JPS58205085A (fr)
KR (1) KR840004571A (fr)
AU (1) AU1397883A (fr)
CA (1) CA1196909A (fr)
ES (1) ES522237A0 (fr)
ZA (1) ZA833020B (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0459414A1 (fr) * 1990-05-30 1991-12-04 Mitsubishi Jukogyo Kabushiki Kaisha Appareil de gazéification du type pressurisé
WO2007116045A1 (fr) * 2006-04-12 2007-10-18 Shell Internationale Research Maatschappij B.V. Appareil et procédé de refroidissement de gaz chaud

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017156025A (ja) * 2016-03-02 2017-09-07 東京電力ホールディングス株式会社 熱交換システム

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR485126A (fr) * 1916-04-26 1917-12-13 Oerlikon Maschf Échangeur de chaleur tubulaire
US2862694A (en) * 1956-01-06 1958-12-02 Phillips Petroleum Co Heat exchanger
FR1405960A (fr) * 1964-06-03 1965-07-16 D Applic Mecaniques Soc Ind Dispositif d'étanchéité, applicable aux échangeurs tubulaires à surface
US3312063A (en) * 1965-07-22 1967-04-04 James H Anderson Heat transfer at equalized pressure
BE686934A (fr) * 1965-10-04 1967-02-15
GB1212526A (en) * 1967-06-15 1970-11-18 Foster Wheeler Brown Boilers Improvements in shell and tube heat exchangers
FR2247691A1 (en) * 1973-10-11 1975-05-09 Fives Cail Babcock Series flow through reheater hairpins improves efficiency - HP steam of reactor passes through longer hairpin bank thence inner rank

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0459414A1 (fr) * 1990-05-30 1991-12-04 Mitsubishi Jukogyo Kabushiki Kaisha Appareil de gazéification du type pressurisé
US5230717A (en) * 1990-05-30 1993-07-27 Mitsubishi Jukogyo Kabushiki Kaisha Pressurized gassification apparatus
WO2007116045A1 (fr) * 2006-04-12 2007-10-18 Shell Internationale Research Maatschappij B.V. Appareil et procédé de refroidissement de gaz chaud
US7628121B2 (en) 2006-04-12 2009-12-08 Shell Oil Company Apparatus and process for cooling hot gas
AU2007235916B2 (en) * 2006-04-12 2010-06-17 Shell Internationale Research Maatschappij B.V. Apparatus and process for cooling hot gas
CN101421578B (zh) * 2006-04-12 2011-06-08 国际壳牌研究有限公司 用于冷却热气体的装置和方法

Also Published As

Publication number Publication date
JPS58205085A (ja) 1983-11-29
ES8404502A1 (es) 1984-04-16
AU1397883A (en) 1983-11-17
ES522237A0 (es) 1984-04-16
ZA833020B (en) 1984-05-30
KR840004571A (ko) 1984-10-22
EP0094097A3 (fr) 1984-05-09
CA1196909A (fr) 1985-11-19

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