EP0111615B1 - 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

Info

Publication number
EP0111615B1
EP0111615B1 EP83100230A EP83100230A EP0111615B1 EP 0111615 B1 EP0111615 B1 EP 0111615B1 EP 83100230 A EP83100230 A EP 83100230A EP 83100230 A EP83100230 A EP 83100230A EP 0111615 B1 EP0111615 B1 EP 0111615B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
channel
exchanger system
heating surface
heat
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.)
Expired
Application number
EP83100230A
Other languages
German (de)
English (en)
Other versions
EP0111615A1 (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
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 Gebrueder Sulzer AG filed Critical Gebrueder 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

Links

Images

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.
  • Such a system is known from CH-PS-375 030, in which the channels are annular spaces which are delimited by concentrically interposed partition walls and through which the hot gas coming from a nuclear reactor flows in series.
  • this system is for gases that can be very dirty, such as. B. process gas from coal gasification plants, not very suitable, since the heat exchanger surfaces have to be cleaned frequently and these are not easily accessible in the known system.
  • the frequency of such cleaning increases with the temperature of the hot gases, because the higher the gas temperature, the greater the deterioration in heat dissipation due to deposits on the heating surfaces.
  • this object is achieved by the features of the characterizing part of claim 1.
  • the particular advantage is achieved 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, its temperatures can be influenced differently. In the system according to the invention, there is also good accessibility to the heat exchanger surfaces during cleaning and, if necessary, repair work.
  • 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 4 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 5 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 6 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 9 shows means which allow to influence the final temperature of the primary gas.
  • the solution according to claim 10 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. Moreover, this solution allows a cross flow in the branching area without a high pressure drop occurring.
  • the features of claim 11 allow an impairment of the heat transfer due to deposits on the evaporator heating surface to be corrected in a simple manner.
  • 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 13.
  • 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.
  • a cylindrical partition 14 is tightly connected, which is connected at its lower end to the wall of the lower part 2 via a tight but easily releasable connection 16.
  • Extending within the circular cylinder formed by the chuck 10 with a small radial distance from the chuck 10 is an outer channel wall 20, which forms a tube section and ends below the ring plate 12.
  • a middle channel wall 22 Arranged within the cylindrical surface formed by the outer channel wall 20 is a middle channel wall 22, which ends at approximately the same height as the outer channel wall 20. Above, 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 and is closed at the top with a hollow elk 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 are designated 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 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 sheets 38.
  • the tube legs are spaced apart from one another by cams, not shown in the drawing, attached to the legs or by ribs running all around at different heights.
  • the tube sheets 38 are layered on the inner channel wall 28, bent into 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 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 exit the above-mentioned ring channel in a practically gas-tight passage and emerge laterally through the wall of the lower part 2 from the pressure vessel 1 via temperature compensation nozzles - known under the name “thermosleeves”.
  • 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.
  • two diametrically offset circular openings 80 are provided in the ring plate 12, below which a valve cone 82 is arranged coaxially to the associated opening 80 on each valve rod 81.
  • Each valve rod 81 is guided in arms 83 fastened to the partition wall 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 rotatably supported in a sleeve 86.
  • 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 distributors 75. 75 ', which comes, for example, from cooling devices or a boiler system.
  • the heat exchanger system according to FIGS. 1 to 4 functions 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 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 member 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 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; therefore, a steam water mixture 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. A lot of heat is emitted in the channel section 30, 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 danger 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 mixing a relatively large amount of hot gas over the Openings 80 raise the temperature of the gas emerging from the pressure vessel 1 to the desired level.
  • 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 helicopter bundle 62 can be inspected from the inside and also 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.
  • the heat exchanger surfaces are shown in the simplest form. Of course, they can also be subdivided and the flow directions reversed in whole or in part.
  • 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, in particular in the superheater pipe bundle, where higher temperatures occur, it may be expedient to connect the connecting pipes 72 according to CH-PS-384 602 to pipe plates.

Landscapes

  • 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)

Claims (13)

1. Système de transfert thermique pour dissiper de la chaleur sensible d'un gaz chaud, de préférence d'un gaz industriel, vers plusieurs surfaces de transfert thermique (36, 62) qui sont disposées dans des canaux et dont l'une consiste en une surface chauffante (36) d'évaporation et une autre consiste en une surface chauffante (62) de transfert thermique dans laquelle un fluide est chauffé, toutes les surfaces de transfert thermique (36, 62) précitées étant renfermées par un seul et unique réservoir de pression (1) sensiblement cylindrique, caractérisé par le fait que le canal (30) qui est tout d'abord parcouru par le gaz chauf forme un tronçon renfermant la surface chauffante (36) d'évaporation et se scindant en deux canaux parallèles de dérivation (32, 34), qui débouchent dans une chambre commune de mélange et dont l'un (32) est aligné avec le tronçon de canal (30) ; par le fait que l'un des deux canaux de dérivation (32, 34) loge une autre surface chauffante (38) de transfert thermique dans laquelle de la chaleur est transmise au fluide provenant de la surface chauffante (36) d'évaporation ; par le fait que l'autre surface chauffante (62) de transfert thermique se trouve dans l'autre canal de dérivation ; et par le fait qu'au moins l'un des deux canaux de dérivation (32, 34) présente un organe réglable d'étranglement (25).
2. Système de transfert thermique selon la revendication 1, caractérisé par le fait que le tronçon de canal (30) et les deux canaux de dérivation (32, 34) sont réalisés sous la forme de canaux annulaires coaxiaux au réservoir de pression (1).
3. Système de transfert thermique selon la revendication 2, caractérisé par le fait que le tronçon de canal (30) et le canal de dérivation (32) qui est aligné avec lui forment un canal annulaire situé le plus à l'intérieur.
4. Système de transfert thermique selon la revendication 3, dont le réservoir de pression (1) présente un axe vertical, caractérisé par le fait que la surface chauffante (36) d'évaporation et l'autre surface de transfert thermique sont réalisées sous la forme d'une unique surface chauffante tubulaire en serpentin, s'étendant tant sur le tronçon de canal (30) que sur le canal de dérivation (32) qui est aligné avec lui ; et par le fait que les canalisations en serpentin de cette surface chauffante s'étendent selon les faisceaux tubulaires (38) cintrés en développante, avec des branches parallèles à l'axe du réservoir de pression.
5. Système de transfert thermique selon la revendication 4, caractérisé par le fait que l'autre surface de transfert thermique (62) située dans l'autre canal de dérivation (34) est réalisée sous la forme d'une surface chauffante hélicoïdale.
6. Système de transfert thermique selon l'une des revendications 2 à 5, caractérisé par le fait que l'organe d'étranglement (25) est réalisé en tant que soupape centrale à disque et se trouve, côté gaz, en aval de la surface de transfert thermique (36) située dans le canal de dérivation (32) aligné avec le tronçon (30), en coiffant simultanément un canal central cylindrique occulté.
7. Système de transfert thermique selon l'une des revendications 4 à 6, caractérisé par le fait que le réservoir de pression (1) présente en partie basse un raccord coaxial de pénétration des gaz, ainsi que, également dans la région inférieure de ce réservoir de pression, au moins un raccord latéral (5) de sortie des gaz.
8. Système de transfert thermique selon les revendications 1 à 7, caractérisé par le fait que la chambre de mélange est reliée au raccord (5) de sortie des gaz du réservoir de pression, par l'intermédiaire d'une chambre annulaire (9) prévue entre l'autre canal de dérivation (34) et la paroi interne dudit réservoir de pression (1).
9. Système de transfert thermique selon la revendication 8, caractérisé par le fait qu'il est prévu, au voisinage de la zone de dérivation du tronçon de canal (30), au moins un orifice (80) qui gagne la chambre annulaire (9) à partir de la région extrême du tronçon de canal (30) ; et par le fait qu'un organe réglable d'obturation (82) est associé à cet orifice (80).
10. Système de transfert thermique selon la revendication 4, caractérisé par le fait que, dans le tronçon de canal (30) et au voisinage de la zone de dérivation, les canalisations en serpentin ont un diamètre considérablement plus petit par rapport à la longueur restante de ces canalisations.
11. Système de transfert thermique selon l'une des revendications 1 à 10, caractérisé par le fait que l'achèvement de la paroi externe (14) du tronçon de canal (30) et/ou le début de la paroi (22) séparant les deux canaux de dérivation (32, 34) sont réalisés réglables dans le sens axial.
12. Système de transfert thermique selon les revendications 4 et 10, caractérisé par le fait que les canalisations en serpentin sont espacées les unes des autres par l'intermédiaire de protubérances qui y sont fixées.
13. Système de transfert thermique selon les revendications 4, 10 et 12, caractérisé par le fait que les faisceaux tubulaires (38) sont suspendus à des branches tubulaires (51, 57) par l'intermédiaire desquelles le fluide est délivré auxdits faisceaux tubulaires ou en est évacué.
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
CH6846/82A CH662638A5 (de) 1982-11-24 1982-11-24 Waermeuebertragersystem, vorzugsweise fuer ein prozessgas.
CH6846/82 1982-11-24

Publications (2)

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

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH665274A5 (de) * 1984-07-05 1988-04-29 Sulzer Ag Waermeuebertrager.
CH665020A5 (de) * 1984-08-15 1988-04-15 Sulzer Ag Waermeuebertrager.
WO2003056265A1 (fr) * 2001-12-25 2003-07-10 Honda Giken Kogyo Kabushiki Kaisha 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

Family Cites Families (11)

* 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
US3279439A (en) * 1964-06-05 1966-10-18 Babcock & Wilcox Co Vapor generating superheating and reheating unit
CH482982A (de) * 1967-10-30 1969-12-15 Sulzer Ag Durch Abhitze beheizter Zwanglaufdampferzeuger
US3766892A (en) * 1972-04-21 1973-10-23 Combustion Eng Split feed economizer
US3884297A (en) * 1973-02-12 1975-05-20 Automotive Environmental Syste Annular flow heat exchanger
CH586372A5 (fr) * 1974-12-06 1977-03-31 Sulzer Ag
US4073267A (en) * 1975-10-03 1978-02-14 General Atomic Company Vapor generator
US4284134A (en) * 1978-09-05 1981-08-18 General Atomic Company Helically coiled tube heat exchanger
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

Also Published As

Publication number Publication date
CH662638A5 (de) 1987-10-15
CA1215968A (fr) 1986-12-30
US4494484A (en) 1985-01-22
DE3364790D1 (en) 1986-09-04
EP0111615A1 (fr) 1984-06-27
JPS5997404A (ja) 1984-06-05

Similar Documents

Publication Publication Date Title
DE2008311B2 (de) Waermetauscher
EP1219892B1 (fr) Chaudière de récupération pour le refroidissement d'un gaz de synthèse chaud
EP0111615B1 (fr) Système de transfert de chaleur, de préférence pour un gaz de processus
DE2517693C2 (de) Als Längsgegenstromapparat ausgebildeter Wärmeaustauscher
EP0160161A1 (fr) Echangeur de chaleur pour refroidir des gaz
CH670501A5 (fr)
EP0366606B1 (fr) Refroidisseur de gaz chauds pour une installation de gazéification de charbon
DE3007610C2 (de) Wärmetaucher mit einer zentralen Einlaßkammer und darunter liegender Auslaßkammer für ein wärmeabgebendes Medium
EP0166805B1 (fr) Système de transfert de chaleur
CH667521A5 (de) Russblaeser.
CH643649A5 (de) Heissgaskuehler mit einem druckbehaelter.
DE2208397A1 (de) Dampfgenerator
DE2459472B1 (de) Gasbeheizter dampferzeuger, insbesondere fuer kernreaktoranlagen
EP0172363B1 (fr) Appareil échangeur de chaleur, en particulier pour refroidir les gaz d'un réacteur à haute température
EP0171558B1 (fr) Appareil échangeur de chaleur
DE2700563C3 (de) Wärmeübertrager für einen Hochtemperaturreaktor
DE544455C (de) Einrichtung zur Dampfzufuehrung an direkt geheizten Zellstoffkochern mit zwangslaeufigem Umlauf der Kochfluessigkeit
DE2854499C2 (de) Gasbeheizter Geradrohr-Dampferzeuger in Elementbauweise für eine Kernreaktoranlage
DE2903644C2 (de) Wärmetauscher für eine gasgekühlte Kernreaktoranlage
DE2654948C2 (de) Tauch-Wärmeaustauscher
DE7829577U1 (de) Speicherbehaelter zur warmwasserbereitung
DE3809265C2 (fr)
DE57267C (de) Destillirkolonne
DE3820947A1 (de) Wirbelschichtreaktor
DE1614360B2 (de) Kernreaktor mit einem druckbehaelter, in dem die spaltbaren elemente in langgestreckten kuehlrohren untergebracht sind

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): BE DE FR GB IT NL

RBV Designated contracting states (corrected)

Designated state(s): BE DE FR GB IT NL

17P Request for examination filed

Effective date: 19841208

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): BE DE FR GB IT NL

REF Corresponds to:

Ref document number: 3364790

Country of ref document: DE

Date of ref document: 19860904

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
ITPR It: changes in ownership of a european patent

Owner name: TRASFORMAZIONE SOCIETARIA;SULZER AKTIENGESELLSCHAF

NLT1 Nl: modifications of names registered in virtue of documents presented to the patent office pursuant to art. 16 a, paragraph 1

Owner name: SULZER AG TE WINTERTHUR, ZWITSERLAND.

NLS Nl: assignments of ep-patents

Owner name: ABB MANAGEMENT AG TE BADEN, ZWITSERLAND.

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

Ref country code: FR

Ref legal event code: CD

BECH Be: change of holder

Free format text: 940420 *ABB MANAGEMENT LTD

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19961212

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19961216

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19961217

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19961219

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19961223

Year of fee payment: 15

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980113

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19980131

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980131

BERE Be: lapsed

Owner name: ABB MANAGEMENT LTD

Effective date: 19980131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980801

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19980113

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19980801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19981001

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST