US3802497A - Heat exchanger for cooling gases - Google Patents

Heat exchanger for cooling gases Download PDF

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Publication number
US3802497A
US3802497A US00117242A US11724271A US3802497A US 3802497 A US3802497 A US 3802497A US 00117242 A US00117242 A US 00117242A US 11724271 A US11724271 A US 11724271A US 3802497 A US3802497 A US 3802497A
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Prior art keywords
floor
fire tubes
tubes
heat exchanger
fire
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US00117242A
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English (en)
Inventor
J Munster
J Scharfen
G Wellensiek
J Kummel
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D51/00—Auxiliary pretreatment of gases or vapours to be cleaned
    • B01D51/10—Conditioning the gas to be cleaned
    • 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
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/40—Shell enclosed conduit assembly
    • Y10S165/401—Shell enclosed conduit assembly including tube support or shell-side flow director
    • Y10S165/405—Extending in a longitudinal direction
    • Y10S165/407—Extending in a longitudinal direction internal casing or tube sleeve
    • Y10S165/408—Tube sleeve

Definitions

  • the invention is therefore based upon the problem of providing an apparatus for the cooling especially of fresh cracking gases which ensures a constant uniform cooling effect with any desired construction size, that is to say gas throughput, gas temperatures and gas pressure of any desired magnitude.
  • Favourable operating conditions are present in the case of an annular arrangement of the fire tubes and supply of the cooling medium through a central descending pipe.
  • a limitation of the number of fire tubes to one row of tire tubes is provided here. From the one row of fire tubes then arranged in a circle it is clear that the necessary equal operating conditions are obtained for all fire tubes.
  • the equal gas fiows in the fire tubes in the case of circular arrangement of the fire tubes, and the ordinary hot gas inlet widening conically'towards the fire tubes, is explained by the fact that the flow conditions in the inlet are substantially rotation-symmetrical in relation to the central axis.
  • the inlet openings of the circularly arranged fire tubes are charged from a gas supply aligned with the fire tubes only with gas of equal flow behaviour, so that with equal tube dimensions and surface qualities in the fire tubes, equal flow conditions establish themselves.
  • the rotation-symmetrical flow conditions in the widening of the gas supply circuit may be assisted by a baffle which is situated in the inlet upstream of the fire tubes.
  • the baffle is preferably made conical and adapted in such a way to the widening, that is to say fills the widening to such extent, that the latter with a gas pressure of 1.6 to 1.8 atm.abs. produces a chamber loading which amounts at maximum to 125 mg/sec/- cum and at least 90 kg/sec/cu.m.
  • the baffle directs the gas directly into the fire tubes and thus advantageously prevents the return eddies which occur in conventional cracking gas supply systems, so that diffusor angles between 60 and 100 easily become possible for the conical widening of the gas inlet.
  • This property makes the baffle, irrespective of the particular arrangement of the fire tubes, likewise suitable for conventional gas supply conduits and cooling devices for gas.
  • the displacement body is also particularly advantageous for cooling devices with fire tubes which are retained at their inlet ends in one common upstream floor.
  • the baffle has the additional effect that it imparts to the upstream floor a larger heat-emitting area than heat absorbing area and thus extra-ordinarily good cooling.
  • the baffle is preferably so formed that the heat-emitting area of the upstream floor is at least twice as large as its heat absorbing area.
  • the baffle reinforces the common floor of the fire tubes in such a way that it can be extremely thin. In this case a bending resistance is imparted to the upstream floor which prevents unacceptable bulging out of the floor under the action of the cooling medium pressure and on heating.
  • a cup-shaped thickening of the floor on its side facing the coolant supply pipe will contribute to this bending resistance.
  • the thickening of the floor then has the additional advantage that it improves the distribution of the cooling medium, issuing from the supply pipe, to the individual fire tubes.
  • the equal cooling effect upon the fire tubes is kept constant by an unambiguous and stable circulation of the cooling medium.
  • cooling medium there serves according to choice liquid lead, liquid sodium and especially water in natural circulation.
  • the fire tubes as known per se, are held at their inlet ends and at their outlet ends in common upstream and downstream floors and with an intermediate floor which encloses the coolant supply pipe and is spaced from the upstream floor.
  • the intermediate floor may conduct the cooling medium issuing from the supply pipe against and according to choice over the entire upstream floor and/or in case of need even to a particular extent upon heavily heated surfaces of the upstream floor.
  • the intermediate floor may provide guide tubes which surround each fire tube in the region of maximum heat-flux density.
  • the guide tubes ensure that the rising cooling medium flows securely along on the fire tubes and intensively cools them.
  • the guide tubes together with the intermediate floor form dirt pockets in which scale and the like impurities can collect, so that these are not deposited in thermally insulating manner on the upstream, that is the lower, floor.
  • the dirt pockets are of such size that their cleaning is not necessary during what is called the tour time of the apparatus.
  • a regular washing off of the interspace between the upstream floor of the fire tubes and the intermediate floor is optionally also provided, in order to prevent deposits on the upstream floor and thus deterioration of the heat transmission to the cooling water.
  • a washing and water drain-off system is arranged between the lower floor and the intermediate fioor for the washing.
  • the fire tubes may be formed over a part of their length as double walled tubes, the cavity between the inner and outer walls being sealed off both against the cooling medium and against the hot gas.
  • the thermal conductivity in the tube wall of the fire tubes is reduced to such an extent that the temperature of the internal wall lies above the maximum occurring condensation point of the gas, while the temperature of the outer wall lies substantially below the temperature pertaining to the maximum condensation point, and depositing of gas leading, say, to petroleum-coke separations is prevented.
  • Each cooling device according to the invention especially in the case of only one row of fire tubes arranged in circular form, has a limited cooling performance which is taken into consideration in modern cracking gas generators such for example as pyrolysis furnaces by a parallel connection of several heat exchangers.
  • This has the additional advantage that the inflowing cracking gas is distributed to the individual heat exchangers and thus the flow conditions are already favourably influenced.
  • each of these tubes is provided with at least one heat exchanger.
  • each tube is preferably provided with four heat exchangers connected in parallel with one another and together forming a cooler section.
  • a horizontal or especially slightly inclined arrangement of the fire tubes is optionally foreseen.
  • the horizontal and slightly inclined arrangement permits, for example in the case of pyrolysis furnaces, of setting up the entire-apparatus for the cooling of the fresh cracking gas, hereinafter called cracking gas cooler, beneath the cracking furnace.
  • the horizontal arrangement of the fire tubes is much simpler in production and maintenance than a vertical arrangement.
  • a further development of the apparatus according to the invention consists in the provision of at least two series-connected heat exchangers with a gas exit temperature of below 500C. for the first heat exchanger.
  • the construction style of the second heat exchanger is of subordinate importance, for below 500C the cracking gas no longer reforms, so that several heat exchangers connected in parallel can be provided with one series-connected common heat exchanger, and this may possibly also take place even in the case of an over-long time of sojourn of the cracking gas in the series-connected heat exchanger.
  • FIG. 1 shows the overall side view of an apparatus
  • FIG. 2 shows a partial elevation, partial longitudinal section of the apparatus of FIG. 1;
  • FIG. 3 is a section taken on the line III-III in FIG.
  • FIG. 4 is a section showing a fire tube of another apparatus
  • FIG. 5 is a section taken on the line VV in FIG. 1;
  • FIG. 6 shows in diagrammatic representation a part of an overall production plant for cracking gas
  • FIG. 7 shows the fire tube of a third apparatus
  • FIG. 8 shows a fourth apparatus for the cooling of fresh cracking gases having several parallel-connected heat exchangers and one series-connected common heat exchanger, in plan view;
  • FIG. 9 shows the apparatus according to FIG. 8 in a view in the direction IX-IX in FIG. 8;
  • FIG. 10 shows a heat exchanger according to FIG. 8 in an individual view.
  • FIGS. 1 and 5 a cooling apparatus is shown which consists of four heat exchangers 1 connected in parallel with one another.
  • the heat exchangers 1 are at the same time arranged three-dimensionally parallel with one another and connected with one another through lugs 2 and bolts 22 at two positions lying one above the other in each case, for assembly.
  • the heat exchangers l are suspended on suitable connectors, cables or the like devices and the lower bolts 22 are released in each case, so that the heat exchangers l with adequate freedom of movement are mounted for swinging in the upper lugs 2 and bolts 22.
  • displacements and variations of dimension of the heat exchangers occurring as a result of thermal expansion are very simply compensated.
  • the heat exchangers 1 are provided in the upper and especially in the lower region with tie-bolts 23.
  • the arrangement of the tie-bolts 23 in the lower region here has the advantage that on heating the heat exchangers expand upwards and thus bending of the transfer conduits leading to the heat exchangers l, which are subject to a substantially higher thermal stressing than the transfer conduits leading away from the heat exchangers 1, is prevented.
  • the four heat exchangers 1 together form a so-called cooler section.
  • a pyrolysis furnace 24 generating a cracking gas
  • each so-called cracking gas pipe 25 conducting away cracking gas there is allocated a cooler section.
  • the fresh cracking gas is here fed within a cooler section to the heat exchangers l at a temperature of between 830 and 850C and a pressure of between 1.6 and 1.8 atm'.abs. by way of a distributor device 3 and pipes 4 from the associated cracking gas pipe 25.
  • the distributor device 3 consists of an inlet flange 6 which is connected with a corresponding flange 5 of the cracking gas pipe 25, and of a dome 7 adjoining the inlet flange 6 and connecting the pipes 4 with the inlet flange 6.
  • the pipes 4 open or widen into gas-distributor cones 8.
  • the gas distributor cones 8 terminate according to FIG. 2 in each case in a cylindrical recess 9 of a container 10 and are connected with the container 10 in sealed manner by means of a sealing ring 11 and a bellows 12, which at the same time has the task of compensating thermal expansions and possibly also production tolerances.
  • the bellows 12 is here connected with a conduit 21 which conducts away the so-called leakage gas which penetrates past the sealing ring 11 into the bellows 12.
  • the container 10 consists essentially of a tubular pressure jacket 13, two floors 14 and 15 and five to twelve cooling pipes, designated as fire tubes 16, which as shown in FIG. 3 are arranged in uniform distribution with one another, parallel with the longitudinal axis of the container 10 and in circular form.
  • the fire tubes 16 are welded into the floors 14 and 15 so that the cracking gas flowing out of the associated distributor cone 8 flows through passage holes 17 of the floor 14, which connect the fire tubes 16 with the distributor cone 8, into the fire tubes 16 at the rear end, in the direction of flow, of the container 10.
  • baffle body 18 is arranged in the distributor cone 8 and in the direction flow of the cracking gas before the floor l4 and has a form conducting the cracking gas to the passage holes 17, which form in the present case is that of a cone with circular base area pointing with its apex into the distributor cone 8.
  • the cracking gas flows through the fire tubes 16, and by contact with the cooled tube wall of the fire tubes 16, within to milliseconds, loses so much heat that a temperature of 500 to 550C is reached and the chemical condition of the cracking gas is frozen, that is to say re-formation of the cracking gas is prevented.
  • the cooling of the fire tubes 16 takes place according to FIG. 2 in a manner in which cooling medium, in this case water, is conducted through a central, supply pipe 19 between the floors l4 and 15, which form a closed space with the pressure jacket 13 of the container 10. At the end facing the floor 14 the supply pipe 19 is connected with an intermediate floor 20 which surrounds the fire tubes 16 with guide tubes 31 with an interval adequate for the water throughflow for their cooling.
  • cooling medium in this case water
  • the water flows in natural circulation upwards through the container formed by floors 14 and 15 and the pressure jacket 13, that is to say when the space formed by the floors l4 and 15 and the pressure jacket 13 is filled with water, the water is warmed on the common floor 14 and on the fire tubes 16.
  • the water experiences a corresponding upward thrust so that it flows along the vertically arranged fire tubes 16 through the guide tubes 31 and continuously cools the tubes 16.
  • the heating of the water on the common floor 14 and the fire tubes 16 leads to steam formation.
  • the water takes up very large quantities of heat on the fire tubes 16 and the floor 14.
  • the steam formation reinforces the flow on the fire tubes 16, in contrast to the known cooling devices.
  • Particularly favourable cooling conditions are present on the floor 14 if with adequate base area of the distributor cone 8 the ratio of the heat emitting surface to the heat absorbing surface is greater than 2.
  • the heat emitting surface is the surface of the floor 14 charged with cooling medium, while the heat absorbing surface is the surface of the floor 14 charged with cracking gas.
  • the guide tubes 31 together with the intermediate floor 20 at the same time act as dirt pockets in which scale and the like impurities can collect. This prevents these impurities from settling in thermally insulating manner on the floor 14 to be cooled and deteriorating the heat transmission between floor 14 and cooling medium.
  • the cooling medium rising as a water-steam mixture is fed through overflow pipes 32, which are connected in the direction of flow of the cracking gas directly upstream of the floor 15 to corresponding openings in the pressure jacket 13, to a known evaporation drum 51, while at the same time boiling water fills up from the evaporation drum through the supply pipe 19.
  • a washing and drainage outlet 33 is fitted to the pressure jacket 13 between the floor 14 and the intermediate floor 20, which outlet consists of a pipe and a shut-off slide valve or cock (not shown).
  • the conduit 35 opens with the conduits 35 of the other three heat exchangers 1 into a collector device 36 which is assembled similarly to the distributor device 3 and recombines the cracking gas current previously divided by the distributor device 3, in order to feed it to a further cooler section or to a processing apparatus.
  • fire tubes are welded in as partially double tubes, namely with an inner tube 42 and an outer tube 43.
  • the fire tubes are formed as double tubes especially in the upper part and over two-thirds of their length.
  • the inner tubes 42 and the outer tubes 43 are tightly connected with one another, for example by welding, with a common transition part 44. While the fire tubes then are connected in the same way as according to FIGS. 1 to 3 with the lower floor 40, which is upstream in the direction of flow of the cracking gas, the fire tubes are tightly connected at their other ends only at by outer tube 43 to the upper floor 41.
  • the inner tubes 42 of the fire tubes are conducted out through the upper floor 41 and are tightly connected with a corresponding flange or floor 45 of the gas collector hood, which is not further illustrated in this case.
  • the heat exchanger according to FIG. 4 differs otherwise from the heat exchangers 1 according to FIGS. 1 to 3, apart from in the fire tubes, essentially only by the supply of the cooling medium, that is to say in the formation of the supply pipe.
  • the de scending pipe 47 consists of a short pipe piece which, with similar intermediate floor 20 and guide tubes 31, is provided with an additional floor 48 at the end remote from the floor 40.
  • the additional floor 48 serves to separate the heated cooling medium from the inflowing cooling medium and thus to prevent intermixing of the two media.
  • FIG. 7 similarly to FIG. 4, a fire tube formed as double tube is shown.
  • the inner tube 42 is pushed into the outer tube 43 and rolled thereto at its lower end to such extent that at this point it is firmly and at the same time sealingly connected with the outer tube 43.
  • the gas collector hood 34 is tightly connected with the container 10, while the inner tube 42, with outer tube 43 firmly and sealingly welded with the upper floor 15, extends out beyond the upper floor and is displaceably mounted in a further floor 53 which is arranged above the upper floor in the gas collector hood 34.
  • the displaceable mounting of the inner tube 42 in the further floor 53 serves for the compensation of its thermal expansion, while the floor 53 in turn serves to protect a sealing composition, which fills out the interspace between the floors 53 and 15 and in doing so encloses the inner tube 42, against the inflow of the cracking gas.
  • three cracking gas pipes 60, 61 and 62 of the pyrolysisfurnace 24 open into three cooler sections 63, 64 and 65 each of which consists of four parallel-connected heat exchangers 66 slightly inclined towards the cracking gas flow, so that to each cracking gas pipe 60, 61, 62 there is allocated a heat exchanger 66.
  • the heat exchangers 66 in turn all open into a gas collector 67 which feeds cracking gas issuing from the heat exchangers 66 and cooled to 450C to a subsequently placed heat exchanger 68.
  • One common cooling water circulation 70 represented in dot-and-dash lines is provided for all the heat exchangers 66 and 68.
  • the heat exchangers 66 and the heat exchanger 68 constructed analogously with the heat exchanger 1, consist each of a number of fire tubes 75 arranged in annular form around a central supply pipe 71 and provided with a triple jacket'72, 73, 74, and of two cylindrical housing chambers 76 and 77.
  • the housing chamber 77 is situated at the upstream end, in the direction offlow of the cracking gas, of each heat exchanger 66 and 68.
  • the housing chamber 77 has two end walls, of which the rear wall encloses the tubes 74 of the fire tube jacketing and the supply pipe 71 as a common floor 78, whilethe forward end wall 79 has the same function as the floor 14 of the heat exchanger 1.
  • the housing chamber 76 is situated at the rear end of the heat exchangers 66 and 68 and is'further divided by an'interme diate wall 80 into a forward chamber 90 and a rear chamber 91.
  • the-tubes 74 of the fire tube jacketing open into the forward chamber 90 and the descending pipe 71 opens into the rear chamber 91, while the tubes 73 are conducted through the rear chamber 91.
  • heat exchangers 66 and 68 differ from the heat exchanger 1 only in that the intermediate space between the gas distributor cone and the bellows is partially filled with a sealing composition.
  • a leakage conduit 84 is connected to the remaining free part of the interspace between the gas distributor cone and the bellows. Steam can be injected additionally through the leakage conduit 84, preventing escape of cracking gas at the point of contact, additionally sealed by a packing ring 85, between the gas distributor cone and the end wall 79 if the packing ring should be damaged.
  • the water drainage and washing outlet designated in this case by 86, is expediently situated at the lowermost point of the housing chamber 77.
  • tie-rods or constant suspensions necessary for the swinging and expansion-compensating mounting of the heat exchangers 66 and 68 are secured with the aid of straps and supports to the heat exchangers 66 and 68 in such a way that each heat exchanger 66 or 68 is suspended at two points.
  • the heat exchangers 66 are connected with one another in the individual cooling sections 63, 64 and 65 through lugs 94 and bolts 95 which are removed after assembly.
  • a heat exchanger for cooling cracking gases comprising a single annular row of vertically arranged laterally spaced fire tubes for conducting hot cracking gases therethrough first means for enclosing said row of fire tubes and forming a cooling passageway for passing a cooling medium over the exterior of said fire tubes, said first means comprising a vertically arranged jacket laterally enclosing said row of fire tubes, an upstream floor extending transversely of and secured to said jacket and the lower ends of said fire tubes secured to and communicating through said upstream floor, a downstream floor extending transversely of and secured to said jacket and the upper ends of said fire tubes secured to and communicating through said downstream floor, an intermediate floor extending transversely of said jacket between said upstream and downstream floors and located adjacent said upstream floor, said fire tubes extending through said intermediate floor, second means including a supply pipe for supplying the cooling medium for flow over said fibre tubes, said supplypipe being vertically arranged and disposed centrally within said row of fire tubes, said supply tube extending downwardly through said downstream floor and having its outlet end
  • said third means for introducing hot gases into said fire tubes includes a gas supply pipe spaced axially from and below the inlet ends of said fire tubes, walls forming a closed inlet chamber extending from said gas inlet pipe to the inlet ends of said fire tubes in the lower face of said upstream floor, said gas inlet pipe having its axis disposed centrally of the axes of said fire tubes, said walls forming the inlet chamber include a frustoconically shaped member connected at its smaller diameter end to said gas inlet pipe and having its wider diameter end connected to said upstream floor encircling the outside diameter of said row of fire tubes at their inlet ends, and said conically shaped baffle spaced radially inwardly from said frusto-conically shaped member and extending downwardly from said upstream floor for only a portion of the axial length of said frusto-conically shaped member.
  • a heat exchanger according to claim 2 in which the conical widening of said frusto-conically shaped member is such that with a hot gas pressure of between 1.6 and 1.8 atm.abs., there is produced a chamber loading which amounts to between 90 and 125 kg/sec.- /cu.m.
  • a heat exchanger as set forth in claim 2, wherein the effective heat-emitting area of the upper face of said upstream floor is at least twice as large as its effective heat-absorbing area on the lower face of said upstream floor.
  • a heat exchanger in which the upstream floor has said cup-shaped thickening on its side facing a supply pipe for the cooling medium.
  • a heat exchanger in which a washing and drainage outlet is arranged between the upstream flow and the intermediate floor.
  • a heat exchanger according to claim 7 in which the annular space between inner wall and the outer wall of a fire tube is filled with air.
  • Gas cooling apparatus comprising several heat exchangers constructed substantially as described with reference to claim 1, the several heat exchangers being connected in parallel and/or in series.
  • Apparatus according to claim 12 in which there are at least two parallel-connected heat exchangers with a common heat exchanger connected thereafter.
  • the fire tubes consist of several tubes of which two tubes form a double jacket through which cooling medium flows and/0r two tubes form a thermally insulating jacket.
  • a plant comprising a furnace for producing hot gases and a number of pipes which lead the hot gases away from the furnace for cooling, each of such pipes being connected to a separate heat exchanger according to claim 1, or to a separate gas cooling apparatus according to claim l2.
  • a heat exchanger as set forth in claim 7, wherein the outer wall of said double wall fire tube is sealed to said means for enclosing said fire tubes and said inner wall extends out of the cooling passageway, and a gas collector hood arranged to receive the end of said inner wall which extends outwardly from the cooling passageway.

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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)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00117242A 1970-02-23 1971-02-22 Heat exchanger for cooling gases Expired - Lifetime US3802497A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2008311A DE2008311C3 (de) 1970-02-23 1970-02-23 Wärmetauscher
DE19702025584 DE2025584A1 (fr) 1970-02-23 1970-05-26

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US (1) US3802497A (fr)
BE (1) BE763273A (fr)
DE (2) DE2008311C3 (fr)
FR (1) FR2080704B1 (fr)
GB (1) GB1292777A (fr)
NL (1) NL7101984A (fr)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3540782A1 (de) * 1985-11-16 1987-05-21 Uhde Gmbh Vorrichtung zur endothermen katalytischen spaltung von kohlenwasserstoffen
DE3643303A1 (de) * 1986-12-18 1988-06-30 Uhde Gmbh Vorrichtung zum waermetausch, insbesondere zwischen synthesegas- und kesselspeisewasser
DE3715713C1 (de) * 1987-05-12 1988-07-21 Borsig Gmbh Waermetauscher insbesondere zum Kuehlen von Spaltgasen
DE3822808A1 (de) * 1988-07-06 1990-01-11 Balcke Duerr Ag Waermetauscher mit zwischen zwei rohrplatten angeordneten waermetauscherrohren
DE3842727A1 (de) * 1988-12-19 1990-06-21 Borsig Gmbh Waermetauscher insbesondere zum kuehlen von spaltgas
US5820641A (en) * 1996-02-09 1998-10-13 Mks Instruments, Inc. Fluid cooled trap
US5826647A (en) * 1994-02-09 1998-10-27 Wolfgang Engelhardt Heat exchanger
EP0777098A3 (fr) * 1995-11-28 1998-11-18 American Schack Company, Inc. Echangeur de chaleur amélioré pour applications à haute température
US6197119B1 (en) 1999-02-18 2001-03-06 Mks Instruments, Inc. Method and apparatus for controlling polymerized teos build-up in vacuum pump lines
US6238514B1 (en) 1999-02-18 2001-05-29 Mks Instruments, Inc. Apparatus and method for removing condensable aluminum vapor from aluminum etch effluent
US6488745B2 (en) 2001-03-23 2002-12-03 Mks Instruments, Inc. Trap apparatus and method for condensable by-products of deposition reactions
DE10303570A1 (de) * 2003-01-30 2004-08-12 Helmut Bälz GmbH Wärmetauschereinrichtung zur Erzeugung von Warm- oder Heißwasser
US6845813B1 (en) * 2003-10-13 2005-01-25 Knighthawk Engineering Intra-body flow distributor for heat exchanger
US20070053807A1 (en) * 2004-01-28 2007-03-08 Anne Boer Heat-exchanger for carrying out an exothermic reaction
WO2007116045A1 (fr) * 2006-04-12 2007-10-18 Shell Internationale Research Maatschappij B.V. Appareil et procédé de refroidissement de gaz chaud
US20100010256A1 (en) * 2006-05-23 2010-01-14 Bayer Materialscience Ag Processes for hydrogen chloride oxidation using oxygen
US20140352931A1 (en) * 2013-05-31 2014-12-04 Steve Turner Corrosion Resistant Air Preheater with Lined Tubes

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL7309228A (nl) * 1973-07-03 1975-01-07 Shell Int Research Inrichting en werkwijze voor het koelen van hete gassen.
DE2551195C3 (de) * 1975-11-14 1981-07-02 Schmidt'sche Heissdampf-Gesellschaft Mbh, 3500 Kassel Wärmeaustauscher zum Kühlen von Spaltgasen
DE3206512C2 (de) * 1982-02-24 1985-05-15 L. & C. Steinmüller GmbH, 5270 Gummersbach Gas-/Flüssigkeits-Gleichstromwärmeaustauscher
DE3533219C1 (de) * 1985-09-18 1986-11-13 Borsig Gmbh, 1000 Berlin Rohrbuendelwaermetauscher
FR2629907A1 (fr) * 1988-04-06 1989-10-13 Collard A Trolart G Perfectionnements aux echangeurs thermiques
FR3011556B1 (fr) * 2013-10-09 2015-12-25 Commissariat Energie Atomique Procede de purification d'un gaz de synthese brut issu d'une pyrolyse et/ou gazeification d'une charge de matiere carbonee par destruction de goudrons contenus dans le gaz

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US779741A (en) * 1904-06-10 1905-01-10 Herman J Scheubner Feed-water heater.
US2329658A (en) * 1937-09-01 1943-09-14 Socony Vacuum Oil Co Inc Method of converting petroleum and like oils
US2825463A (en) * 1954-12-31 1958-03-04 Standard Oil Co Thermal diffusion apparatus
US3000193A (en) * 1958-02-21 1961-09-19 Hupp Corp Air conditioning evaporators
US3100697A (en) * 1960-08-01 1963-08-13 Gas Proc Inc Apparatus for treatment of natural gas
US3287090A (en) * 1964-01-02 1966-11-22 Diamond Alkali Co Gas distributor
US3298358A (en) * 1964-12-30 1967-01-17 Combustion Eng Vertical steam generator with a central downcomer
US3610329A (en) * 1968-12-27 1971-10-05 Basf Ag Tube plate for hot gas coolers

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH360844A (de) * 1957-01-30 1962-03-15 Halbergerhuette Gmbh Luftkühler für die Ladeluft von mehrzylindrigen Verbrennungskraftmaschinen
DE1205121B (de) * 1959-05-02 1965-11-18 Scheer & Cie C F Stehender Waermetauscher
FR1332118A (fr) * 1964-04-16 1963-12-16
FR1456440A (fr) * 1964-12-24 1966-05-20 Schmidt Sche Heissdampf échangeur thermique pour le refroidissement de gaz sortant de craquage ou autres
FR1519256A (fr) * 1966-06-13 1968-03-29 Stone & Webster Eng Corp Appareil et procédé de refroidissement
US3387055A (en) * 1966-09-29 1968-06-04 El Paso Products Co Process for quenching iodine-effected dehydrogenation effluent
CH449678A (de) * 1967-06-20 1968-01-15 Bertrams Ag Hch Röhrenwärmeaustauscher mit flüssigem Wärmeträger
US3574781A (en) * 1968-02-14 1971-04-13 Atlantic Richfield Co Transition section for ethylene production unit
DE1751090A1 (de) * 1968-04-02 1971-10-07 Basf Ag Verfahren zur Kuehlung von Spalt- oder Synthesegas und Waermeaustauscher zur Durchfuehrung des Verfahrens
JPS5333561B1 (fr) * 1968-09-12 1978-09-14

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US779741A (en) * 1904-06-10 1905-01-10 Herman J Scheubner Feed-water heater.
US2329658A (en) * 1937-09-01 1943-09-14 Socony Vacuum Oil Co Inc Method of converting petroleum and like oils
US2825463A (en) * 1954-12-31 1958-03-04 Standard Oil Co Thermal diffusion apparatus
US3000193A (en) * 1958-02-21 1961-09-19 Hupp Corp Air conditioning evaporators
US3100697A (en) * 1960-08-01 1963-08-13 Gas Proc Inc Apparatus for treatment of natural gas
US3287090A (en) * 1964-01-02 1966-11-22 Diamond Alkali Co Gas distributor
US3298358A (en) * 1964-12-30 1967-01-17 Combustion Eng Vertical steam generator with a central downcomer
US3610329A (en) * 1968-12-27 1971-10-05 Basf Ag Tube plate for hot gas coolers

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3540782A1 (de) * 1985-11-16 1987-05-21 Uhde Gmbh Vorrichtung zur endothermen katalytischen spaltung von kohlenwasserstoffen
DE3643303A1 (de) * 1986-12-18 1988-06-30 Uhde Gmbh Vorrichtung zum waermetausch, insbesondere zwischen synthesegas- und kesselspeisewasser
DE3715713C1 (de) * 1987-05-12 1988-07-21 Borsig Gmbh Waermetauscher insbesondere zum Kuehlen von Spaltgasen
EP0290813A1 (fr) * 1987-05-12 1988-11-17 Deutsche Babcock- Borsig Aktiengesellschaft Echangeur de chaleur, en particulier pour refroidir des gaz de crackage
US4858684A (en) * 1987-05-12 1989-08-22 Borsig Gmbh Heat exchanger, especially for cooling cracked gas
DE3822808A1 (de) * 1988-07-06 1990-01-11 Balcke Duerr Ag Waermetauscher mit zwischen zwei rohrplatten angeordneten waermetauscherrohren
DE3842727A1 (de) * 1988-12-19 1990-06-21 Borsig Gmbh Waermetauscher insbesondere zum kuehlen von spaltgas
US5826647A (en) * 1994-02-09 1998-10-27 Wolfgang Engelhardt Heat exchanger
EP0777098A3 (fr) * 1995-11-28 1998-11-18 American Schack Company, Inc. Echangeur de chaleur amélioré pour applications à haute température
US5820641A (en) * 1996-02-09 1998-10-13 Mks Instruments, Inc. Fluid cooled trap
US6361607B2 (en) 1999-02-18 2002-03-26 Mks Instruments, Inc. Apparatus for controlling polymerized teos build-up in vacuum pump lines
US6238514B1 (en) 1999-02-18 2001-05-29 Mks Instruments, Inc. Apparatus and method for removing condensable aluminum vapor from aluminum etch effluent
US6197119B1 (en) 1999-02-18 2001-03-06 Mks Instruments, Inc. Method and apparatus for controlling polymerized teos build-up in vacuum pump lines
US20020053191A1 (en) * 1999-02-18 2002-05-09 Youfan Gu Method for removing condensable aluminum chloride vapor from aluminum etch effluent
US6790258B2 (en) 1999-02-18 2004-09-14 Mks Instruments, Inc. Method for removing condensable aluminum chloride vapor from aluminum etch effluent
US6488745B2 (en) 2001-03-23 2002-12-03 Mks Instruments, Inc. Trap apparatus and method for condensable by-products of deposition reactions
DE10303570A1 (de) * 2003-01-30 2004-08-12 Helmut Bälz GmbH Wärmetauschereinrichtung zur Erzeugung von Warm- oder Heißwasser
DE10303570B4 (de) * 2003-01-30 2007-02-01 Helmut Bälz GmbH Wärmetauschereinrichtung zur Erzeugung von Warm- oder Heißwasser
US6845813B1 (en) * 2003-10-13 2005-01-25 Knighthawk Engineering Intra-body flow distributor for heat exchanger
US20070053807A1 (en) * 2004-01-28 2007-03-08 Anne Boer Heat-exchanger for carrying out an exothermic reaction
US8246915B2 (en) * 2004-01-28 2012-08-21 Shell Oil Company Heat-exchanger for carrying out an exothermic reaction
WO2007116045A1 (fr) * 2006-04-12 2007-10-18 Shell Internationale Research Maatschappij B.V. Appareil et procédé de refroidissement de gaz chaud
US20070267171A1 (en) * 2006-04-12 2007-11-22 Herwig Uwe Apparatus and process for cooling hot gas
US7628121B2 (en) 2006-04-12 2009-12-08 Shell Oil Company Apparatus and process for cooling hot gas
US20100010256A1 (en) * 2006-05-23 2010-01-14 Bayer Materialscience Ag Processes for hydrogen chloride oxidation using oxygen
US20140352931A1 (en) * 2013-05-31 2014-12-04 Steve Turner Corrosion Resistant Air Preheater with Lined Tubes
US11149945B2 (en) * 2013-05-31 2021-10-19 Corrosion Monitoring Service, Inc. Corrosion resistant air preheater with lined tubes

Also Published As

Publication number Publication date
DE2008311A1 (fr) 1971-09-09
FR2080704A1 (fr) 1971-11-19
BE763273A (fr) 1971-07-16
DE2008311C3 (de) 1974-03-07
FR2080704B1 (fr) 1974-06-21
DE2008311B2 (de) 1973-08-09
GB1292777A (en) 1972-10-11
DE2025584A1 (fr) 1971-12-09
NL7101984A (fr) 1971-08-25

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