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EP0111615A1 - Système de transfert de chaleur, de préférence pour un gaz de processus - Google Patents

Système de transfert de chaleur, de préférence pour un gaz de processus Download PDF

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Publication number
EP0111615A1
EP0111615A1 EP83100230A EP83100230A EP0111615A1 EP 0111615 A1 EP0111615 A1 EP 0111615A1 EP 83100230 A EP83100230 A EP 83100230A EP 83100230 A EP83100230 A EP 83100230A EP 0111615 A1 EP0111615 A1 EP 0111615A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger system
branch
pressure vessel
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.)
Granted
Application number
EP83100230A
Other languages
German (de)
English (en)
Other versions
EP0111615B1 (fr
Inventor
Wolfgang Ruzek
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.)
ABB Management AG
Original Assignee
Sulzer AG
Gebrueder Sulzer 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 Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of EP0111615A1 publication Critical patent/EP0111615A1/fr
Application granted granted Critical
Publication of EP0111615B1 publication Critical patent/EP0111615B1/fr
Expired 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
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1838—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines the hot gas being under a high pressure, e.g. in chemical installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
    • F22B21/22—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes of form other than straight or substantially straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/007—Control systems for waste heat boilers
    • 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
    • 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 system according to the preamble of claim 1.
  • a heat exchanger system according to the preamble of claim 1.
  • Such a system has been proposed in which the heat exchanger surfaces are accommodated in different pressure vessels. This solution is complicated, expensive and time-consuming to assemble.
  • the heat exchanger system can also be used in the case of very hot process gases and that if the heat transfer changes due to deposits on the heat exchanger surfaces by adjusting the throttle element, the proportional heat transfer at the various heat exchanger surfaces can be varied. By adjusting the supply of the secondary medium, it can then be Influence temperatures differently.
  • the features of claim 2 lead to a solution with a minimum of unused space.
  • the pressure vessel is therefore small and relatively light, which is expressed in a low price, easier transportability and easier and faster assembly.
  • Claim 3 brings considerable structural advantages in that smooth partitions can be provided.
  • Claim 5 makes the invention advantageous in terms of price, since the snake tubes can be produced very easily and the suspension of the tubes does not require any special suspension means.
  • the embodiment according to claim 6 enables the heat exchanger surface accommodated in the other branch duct to be arranged in cocurrent and / or in countercurrent. This results in a particularly high heat transfer and in the event of a leak, the affected pipes can be easily blinded without this leading to hot strands in the primary medium.
  • Claim 7 leads to a simple, relatively small throttle body, which is in a moderate temperature range and can be operated with a very simple drive.
  • the wall of the pressure vessel is protected from excessive temperatures in a simple manner.
  • Claim 10 shows means which allow to influence the final temperature of the primary gas.
  • the solution according to claim 11 has the advantages that in the highest temperature range the heat transfer on the primary side is reduced due to the reduced gas velocity and, conversely, the heat transfer on the secondary side is increased by the higher medium velocity, both of which lead to a reduction in the tube wall temperature. Furthermore, this solution allows a cross flow in the branching area without a higher pressure drop occurring.
  • the snake tubes By means of the spacing by means of cams, the snake tubes can be packed together to form a compact ring bundle that can easily be hung from the outermost tubes, as claimed in claim 14.
  • a tubular lower part 2 with claws 3 is placed on a foundation 4 of a cylindrical pressure vessel 1.
  • the lower part 2 is connected at its lower end to a gas inlet line, not shown.
  • a little gas outlet nozzle 5 is arranged laterally a little above its lower end.
  • the lower part 2 has a flange 6, on which sits a cover 7, which forms the upper part of the pressure vessel 1.
  • an outer channel wall 20 extends with a small radial distance from the chuck 10, which forms a tube section and ends below the ring plate 12.
  • a middle channel wall 22 is arranged within the cylindrical surface formed by the outer channel wall 20.
  • the middle channel wall 22 carries a sheet metal cone 23 with a valve seat 24.
  • a throttle element acts with the valve seat 24 25 together in the form of a poppet valve which is actuated by a servo motor 26.
  • An inner channel wall 28 is provided within the middle channel wall 22, which is also circular cylindrical forms and is closed at the top with a hollow sheet metal cone 27.
  • the channel wall 28 extends downward beyond the middle channel wall 22 far into the region of the partition wall 14.
  • this channel section bifurcates into two branch channels 32 and 34, of which the inner channel 32 as "the one branch channel 32" and the outer channel 32 as “the other branch channel 34" and which are separated from one another by the central channel wall 22.
  • a single coil heating surface 36 which is connected as an evaporator, extends over the entire height of the annular section formed by the channel section 30 and the annular space formed by a branch channel 32.
  • the coil heating surface 36 consists of thirty-six involute-curved tube sheets 38, which are each formed from a tube with vertically directed legs. Such a tube sheet 38 is particularly highlighted in FIGS. 2 and 3 and drawn in an unwound manner in FIG. 4.
  • a vertical leg 51 lying on an outermost tube cylinder 50 (FIG. 3) is connected via an inclined section 52 to a leg 54 lying on an innermost tube cylinder 53.
  • the leg 54 is connected at the top via a manifold to a leg 55 which is connected at the bottom via a manifold to a further leg 56.
  • a leg 57 finally leads vertically upwards, where it, together with the leg 51, penetrates the sheet metal cone 23 via a sealing part (not shown) and leads to the pressure vessel cover 7, which the tube legs 51 and 57 pierce through known sealing sleeves .
  • the legs 51 and 57 are then connected to a distributor 58 and a collector 59 together with the corresponding legs of the remaining thirty-five tube plates 38.
  • the tube legs are spaced apart from one another by cams attached to the legs, not shown in the drawing, or by ribs running all around at different heights.
  • the tube sheets 38 are layered on the inner channel wall 28, bent to involute surfaces and pressed together radially with tension belts, not shown, which extend over the circumference of the coil heating surface 36.
  • the heating surface bundle formed in this way is tightly encased in the region of the one branch duct 32 with a wire mesh and then with the central duct wall 22 welded together / from two half-shells.
  • the outermost pipe limbs 51 rest against the partition 14, which is thereby cooled during operation.
  • a wire mesh made of highly heat-resistant material or an insulation, which reduces the heat transfer to the partition 14 can also be provided here, optionally in several layers. Means for improving the heat transfer can be provided on the outside of the partition wall 14.
  • the heat exchanger surface in the other branch duct 34 is in the form of a helical heating surface 62, which consists of ninety-two helically wound tubes 64, which form five tube cylinders.
  • the pipes 64 are connected to manifolds 75, 75 'via connecting pipes 72 which penetrate the wall of the lower part 2.
  • each pipe 64 is connected via a pipe bend 65 to one of ninety-two riser pipes 66, which run vertically in the annular channel formed between the lining 10 and the outer channel wall 20.
  • the risers leave the ring channel mentioned and emerge laterally through the wall of the lower part 2, through the wall of the lower part 2, via temperature compensation connections - which are known under the name " T hermosleeves".
  • the risers are connected to two collectors 70, 70 '.
  • the tubes 64 of the Helissen heating surface are held in perforated support plates 61, which are arranged within the branch channel 34 in three planes offset by 120 ° from one another and running through the vertical axis of the pressure vessel 1.
  • the upper ends of the support plates are fastened laterally to the wall of the lower part 2 and have 62 bores 63 over the height region of the Helissen heating surface.
  • the tubes 64 are wound into these bores.
  • valve cone 82 is arranged coaxially to the associated opening 80 on a valve rod 81.
  • Each valve rod 81 is guided in arms 83 fastened to the partition 14 and coupled to a fork lever 84 with an elongated hole via a connecting pin (not shown in the drawing).
  • the fork lever 84 sits on a shaft 85 which is rotatable in a sleeve 86 is stored.
  • the sleeve 86 is removably attached to a suitably arranged pressure vessel connector 87.
  • the shaft 85 penetrates a flat cover 88 with a stuffing box 89. It can be rotated from the outside to adjust the height of the valve cone 82.
  • the gas outlet nozzle 5 is lined with a feed plate 92 which forms an inlet nozzle and which leads into a static mixer 93.
  • the partition wall 14, the connection 16 and the lowermost section of the lower part 2 are protected from excessive temperatures by a brick lining 46, which may not contain cooling pipes.
  • the collector 59 is connected via a saturated steam line 45 to a separator 46, the steam outlet line 47 leading to the distributors 75 and 75 ', while separated water is discharged via an outlet connection 48 attached to the bottom of the separator 46.
  • a further steam supply line 49 is connected to the distributor 75, 75 ′, which comes from cooling devices or a boiler system, for example.
  • the heat exchanger system according to FIGS. 1 to 4 works as follows:
  • the pressure vessel 1 is supplied with a process gas of, for example, 1000 ° C. and 20 to 40 bar at its lower end.
  • This gas flows through the channel section 30, whereupon it is distributed to one branch channel 32 and the other branch channel 34 after cooling to approximately 800 ° C. in the height region of the lateral opening between the ring plate 12 and the lower edge of the central channel wall 22.
  • these branch channels there is further heat, - the partial flow in the branch channel 32 being cooled to, for example, 320 ° C. and that in the other branch channel to, for example, 380 ° C.
  • the two gas flows Downstream of the throttle element 25 the two gas flows combine, resulting in a mixing temperature of, for example, 350 ° C.
  • the combined gas flow then passes through the annular space 9, tempering the wall of the pressure vessel, into the annular space below the annular plate 12 and from there through the gas outlet connection 5 for further use.
  • the lining plate 92 In order that the hot gas streaks emanating from the openings 80 neither cause hot spots on the wall of the lower part 2 nor on the gas outlet connection 5, the lining plate 92, optionally supported by additional guide plates, keeps such streaks away from the pressure-bearing wall.
  • the static mixer 93 then makes the gas temperature more uniform.
  • Preheated water is supplied to the heat exchanger system as a secondary medium via the distributor 58 and is fed into the coil heating surface 36 via the legs 51 serving as support tubes.
  • this coil heating surface serves as an evaporator; a steam water mixture therefore flows into the collector 59 via the legs 57.
  • the steam water mixture is then separated in the separator 46; the water is excreted through the nozzle 48, and the saturated steam is fed via line 47 into the distributors 75, 75 '.
  • the heating surfaces in the channel section 30 and the two branch channels 32 and 34 are designed so large with regard to any heating surface contamination that initially it is possible to operate with the throttle element 25 open little and the openings 80 wide open. in the
  • Channel section 30 is emitted a lot of heat, so that the branch channel 32 can be throttled accordingly. Since the inlet temperature in the other branch duct 34 is relatively low, there is no risk that the overheating of the steam will rise too high. In contrast, there is a relatively low mixing temperature of the gas mixture downstream of the two branch channels. By admixing a relatively large amount of hot gas through the openings 80, the temperature of the gas emerging from the pressure vessel 1 is raised again to the desired level.
  • the coil heating surface 36 absorbs too little heat in its lower part, which is caused by a further opening of the throttle member 25 can be corrected. Since the bundle of helicopters 62 is very oversized, there is little risk that the desired superheating temperature will not be reached.
  • the cover 7 is lifted off to clean the heating surfaces, the central duct wall 22, which is suspended from the supporting legs 51, the coil heating surface 36 and the inner channel wall 28 are also pulled out.
  • the middle channel wall 22 can then be relatively easily detached from the cone 23 and separated into two shells so that they can be removed sideways.
  • the tube panels 38 can now be bent slightly outwards, in particular in the middle and lower part of the coil heating surface, so that they can be cleaned.
  • the bundle of helicopters 62 can be inspected from the inside and can also be cleaned from there.
  • the partition wall 14 can easily be raised beyond the ring plate 12 or the middle channel wall 22 shortened or extended downwards.
  • branch point adjustable, for example by one or two ring slides or by a bypass provided in the central channel wall 22.
  • the invention is not limited to the illustrated embodiment.
  • it can also be advantageous to design the channels 30, 32 and 34 at least partially as membrane walls, that is to say from tubes welded to walls.
  • the heat exchanger surfaces are shown in the simplest form. Of course, they can also be subdivided and the flows in whole or in part reverse directions.
  • more than one secondary medium can be involved in the heat transfer. If throttling elements in the pressure vessel are to be avoided, they can also be placed in connecting lines which serve to guide the gas outside the pressure vessel.
  • the quantity distribution of the secondary medium or the secondary media can also be changed under certain circumstances.
  • the invention is by no means bound to the exemplary embodiment shown; for example, pocket pipes or heat pipes can also be used.
  • the branching to the branch channels can be staggered at different temperatures or temperature ranges.
  • the merging of the branch streams can also be staggered.
  • the openings 80 can be connected to points of lower temperature, be it of one or the other branch channel. Depending on the boundary conditions, it can also be expedient to interchange the arrangement of the channels in the pressure vessel or to arrange them in some other way. In order to facilitate the blinding of individual pipes, especially in the superheater pipe bundle, where higher temperatures occur, it can be expedient to connect the connecting pipes 72 according to CH-PS 384 602 to pipe plates.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP83100230A 1982-11-24 1983-01-13 Système de transfert de chaleur, de préférence pour un gaz de processus Expired EP0111615B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH6846/82 1982-11-24
CH6846/82A CH662638A5 (de) 1982-11-24 1982-11-24 Waermeuebertragersystem, vorzugsweise fuer ein prozessgas.

Publications (2)

Publication Number Publication Date
EP0111615A1 true EP0111615A1 (fr) 1984-06-27
EP0111615B1 EP0111615B1 (fr) 1986-07-30

Family

ID=4315941

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83100230A Expired EP0111615B1 (fr) 1982-11-24 1983-01-13 Système de transfert de chaleur, de préférence pour un gaz de processus

Country Status (6)

Country Link
US (1) US4494484A (fr)
EP (1) EP0111615B1 (fr)
JP (1) JPS5997404A (fr)
CA (1) CA1215968A (fr)
CH (1) CH662638A5 (fr)
DE (1) DE3364790D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0166805A3 (en) * 1984-07-05 1986-04-09 Gebruder Sulzer Aktiengesellschaft Heat transfer system

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH665020A5 (de) * 1984-08-15 1988-04-15 Sulzer Ag Waermeuebertrager.
EP1460365A4 (fr) * 2001-12-25 2005-01-05 Honda Motor Co Ltd Echangeur thermique
FR2921718B1 (fr) * 2007-10-01 2014-11-28 Snecma Echangeur thermique de prechauffage pour pile a combustible
US8555809B2 (en) * 2010-01-14 2013-10-15 Rohm And Haas Electronic Materials, Llc Method for constant concentration evaporation and a device using the same
US9366203B2 (en) * 2013-09-24 2016-06-14 Fca Us Llc Conformable high pressure gaseous fuel storage system having a gas storage vessel with fractal geometry
US9957612B2 (en) 2014-01-17 2018-05-01 Ceres Technologies, Inc. Delivery device, methods of manufacture thereof and articles comprising the same

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH174774A (de) * 1934-06-08 1935-01-31 Sulzer Ag Wärmeaustauscher.
CH375030A (de) * 1960-01-29 1964-02-15 Sulzer Ag Wärmeübertrager
CH482982A (de) * 1967-10-30 1969-12-15 Sulzer Ag Durch Abhitze beheizter Zwanglaufdampferzeuger
US3884297A (en) * 1973-02-12 1975-05-20 Automotive Environmental Syste Annular flow heat exchanger
FR2293663A1 (fr) * 1974-12-06 1976-07-02 Sulzer Ag Generateur de vapeur chauffe par gaz, pour centrales nucleaires en particulier
FR2435667A1 (fr) * 1978-09-05 1980-04-04 Gen Atomic Co Echangeur de chaleur a tubes helicoidaux du type utilise comme generateur de vapeur

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3279439A (en) * 1964-06-05 1966-10-18 Babcock & Wilcox Co Vapor generating superheating and reheating unit
US3766892A (en) * 1972-04-21 1973-10-23 Combustion Eng Split feed economizer
US4073267A (en) * 1975-10-03 1978-02-14 General Atomic Company Vapor generator
DE2846581A1 (de) * 1978-10-26 1980-05-08 Ght Hochtemperaturreak Tech Waermetauscher fuer gase von hoher temperatur
US4252087A (en) * 1979-04-24 1981-02-24 Kime Wellesley R Rapid response steam generating apparatus and method

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH174774A (de) * 1934-06-08 1935-01-31 Sulzer Ag Wärmeaustauscher.
CH375030A (de) * 1960-01-29 1964-02-15 Sulzer Ag Wärmeübertrager
CH482982A (de) * 1967-10-30 1969-12-15 Sulzer Ag Durch Abhitze beheizter Zwanglaufdampferzeuger
US3884297A (en) * 1973-02-12 1975-05-20 Automotive Environmental Syste Annular flow heat exchanger
FR2293663A1 (fr) * 1974-12-06 1976-07-02 Sulzer Ag Generateur de vapeur chauffe par gaz, pour centrales nucleaires en particulier
FR2435667A1 (fr) * 1978-09-05 1980-04-04 Gen Atomic Co Echangeur de chaleur a tubes helicoidaux du type utilise comme generateur de vapeur

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0166805A3 (en) * 1984-07-05 1986-04-09 Gebruder Sulzer Aktiengesellschaft Heat transfer system

Also Published As

Publication number Publication date
EP0111615B1 (fr) 1986-07-30
CH662638A5 (de) 1987-10-15
DE3364790D1 (en) 1986-09-04
US4494484A (en) 1985-01-22
JPS5997404A (ja) 1984-06-05
CA1215968A (fr) 1986-12-30

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