US20010042613A1 - Heat exchanger with tubes suspended into a lower end plate allowing thermal movement of the tubes - Google Patents
Heat exchanger with tubes suspended into a lower end plate allowing thermal movement of the tubes Download PDFInfo
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- US20010042613A1 US20010042613A1 US09/449,522 US44952299A US2001042613A1 US 20010042613 A1 US20010042613 A1 US 20010042613A1 US 44952299 A US44952299 A US 44952299A US 2001042613 A1 US2001042613 A1 US 2001042613A1
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- Prior art keywords
- tubes
- tube
- heat exchanger
- bellows
- tube plate
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Links
- 239000006229 carbon black Substances 0.000 claims abstract description 13
- 230000008602 contraction Effects 0.000 claims abstract description 6
- 238000004519 manufacturing process Methods 0.000 claims abstract description 5
- 230000001681 protective effect Effects 0.000 claims description 14
- 238000003466 welding Methods 0.000 abstract description 3
- 239000003570 air Substances 0.000 description 10
- 238000002485 combustion reaction Methods 0.000 description 9
- 238000009413 insulation Methods 0.000 description 8
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 6
- 239000000919 ceramic Substances 0.000 description 6
- 239000007789 gas Substances 0.000 description 5
- 238000013461 design Methods 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 3
- 239000006232 furnace black Substances 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000011214 refractory ceramic Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- UAOUIVVJBYDFKD-XKCDOFEDSA-N (1R,9R,10S,11R,12R,15S,18S,21R)-10,11,21-trihydroxy-8,8-dimethyl-14-methylidene-4-(prop-2-enylamino)-20-oxa-5-thia-3-azahexacyclo[9.7.2.112,15.01,9.02,6.012,18]henicosa-2(6),3-dien-13-one Chemical compound C([C@@H]1[C@@H](O)[C@@]23C(C1=C)=O)C[C@H]2[C@]12C(N=C(NCC=C)S4)=C4CC(C)(C)[C@H]1[C@H](O)[C@]3(O)OC2 UAOUIVVJBYDFKD-XKCDOFEDSA-N 0.000 description 1
- TVTJUIAKQFIXCE-HUKYDQBMSA-N 2-amino-9-[(2R,3S,4S,5R)-4-fluoro-3-hydroxy-5-(hydroxymethyl)oxolan-2-yl]-7-prop-2-ynyl-1H-purine-6,8-dione Chemical compound NC=1NC(C=2N(C(N(C=2N=1)[C@@H]1O[C@@H]([C@H]([C@H]1O)F)CO)=O)CC#C)=O TVTJUIAKQFIXCE-HUKYDQBMSA-N 0.000 description 1
- MYMOFIZGZYHOMD-UHFFFAOYSA-N Dioxygen Chemical compound O=O MYMOFIZGZYHOMD-UHFFFAOYSA-N 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000007792 addition Methods 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 229910010293 ceramic material Inorganic materials 0.000 description 1
- 239000006231 channel black Substances 0.000 description 1
- 229940125851 compound 27 Drugs 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 230000037430 deletion Effects 0.000 description 1
- 238000012217 deletion Methods 0.000 description 1
- 229910001882 dioxygen Inorganic materials 0.000 description 1
- 239000012467 final product Substances 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 239000000843 powder Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000000746 purification Methods 0.000 description 1
- 238000000197 pyrolysis Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 239000004753 textile Substances 0.000 description 1
- 239000006234 thermal black Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 230000001131 transforming effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- 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
- F28F9/02—Header boxes; End plates
- F28F9/0236—Header boxes; End plates floating elements
Definitions
- the present invention relates to a tube heat exchanger and a tube plate for supporting the tubes of a tube heat exchanger. Specifically the invention relates to a heat exchanger with vertical tubes of considerable lengths having weights which in combination with high temperature subject the tubes themselves and the tube plate to considerable stresses. This tube plate is particularly suitable for use in tube heat exchangers which produce carbon black.
- Carbon black is the term used for the finely divided powder forms of carbon which are produced by incomplete combustion or thermic degradation of natural gas or mineral oil.
- different types of carbon black arise, namely so called channel black, furnace black and pyrolysis black (also called thermal black).
- Furnace black is by far the most important form of carbon black and is used to a considerably larger extent than the other two.
- the present invention relates specifically to this type of carbon black, which in the present application is referred to simply as just “carbon black”.
- FIG. 1A illustrates a conventional plant for the production of carbon black (i.e. of the furnace black type).
- Incoming combustion air flows through a tube conduit 1 into the upper part of a tube heat exchanger 2 , in which it is preheated before supporting the subsequent combustion of oil in the burner 9 and the combustion reactor 3 .
- the thus preheated air is passed into the combustion chamber 10 via a conduit 5 .
- Oil is added to said reactor via a tube conduit 4 .
- the amount of air corresponds to about 50% of the stoichiometric amount of oxygen gas required for a complete combustion of the oil, whereby carbon black is formed. It is also possible to add water into the reactor 3 , which has an impact on the quality of the final product.
- the mixture of the suspended carbon black in the consumed combustion air is led away from the top of the heat exchanger via a conduit 6 , through a cooler 7 which is normally water cooled to a filter arrangement 8 , conventionally equipped with textile bag filters.
- a filter arrangement 8 conventionally equipped with textile bag filters.
- the carbon black is filtered off from the gas flow, which is then passed out through a non-return valve 16 for further purification in a plant 11 , before it is exhausted into the ambient air via a chimney 12 .
- the construction of the conventional heat exchanger 2 may be more clearly seen in FIG. 1B.
- the heat exchanger is of the tube type, with a plurality of substantially vertical tubes 13 whose lower ends are supported on a tube plate 5 A.
- the gases from the combustion process rise up the insides of these tubes, whereby they are cooled by the air that enters via the inlet 1 and passes outside the tubes 13 downwards towards the outlet 5 , in the space enclosed by the outer jacket wall 14 .
- the air coming through the inlet 1 is subjected to a reciprocal movement by an arrangement of a plurality of mainly horizontal baffles 15 .
- the temperature at the inlet 1 of the heat exchanger tubes 13 may be about 1000° and the air coming through conduit 1 may be heated to about 800°. These conditions result in utmost severe stresses for the materials in the heat exchanger.
- the part of the heat exchanger that is submitted to the highest mechanical stress is the lower part of the jacket and the tube plate 5 A where the temperature may amount to 900°.
- the tube plate must be able to withstand exceptionally large stresses, particularly since the tubes 13 rest with their entire weight on the tube plate. Furthermore, even the lower portions of the actual tubes 13 are exposed to heavy loads via their own weight in combination with the high temperatures.
- the tubes 13 have individual compensator devices placed at the top of each tube, the function of which is to off-load the thermally induced stresses in the tubes, as a result, for example of clogging.
- the heat exchanger includes a further jacket wall, which is substantially cylindrical and is placed inwards and mainly concentrically to the outer jacket wall so that at both ends open, mainly cylindrical spaces are formed in the gap between the two jacket walls, whereby the gas which flows in through the inlet passes through this space before coming into contact with the tubes of the heat exchanger. Occasionally the tube plate has failed to stand up to the heavy loads to which it has been exposed leading to very high repair costs.
- the manifold 21 be split up into a number of channels through the use of dividing walls, whereby each channel is provided with an inlet and an exhaust, and a number of heat exchange tubes pass through each channel.
- This has solved the problem of excessive temperatures in the base plate in a satisfactory manner, but the lower portions of the heat exchanger tubes are still very hot and can, for example, bend or buckle.
- a 13 m long heat exchanger tube can weigh approximately 100 kg. Since the tube stands with its entire weight on the tube plate, the tube plate and the lower, very hot parts of the tubes are particularly heavily loaded. When a buckle is induced, stress on the tubes increases and the deformation process can accelerate.
- a prime objective of the present invention is thus to produce a heat exchanger in which the lower parts of the tubes are protected from large loads.
- a second objective of the invention in question is even to protect the lower tube plate from large loads.
- the heat exchanger so as to include a substantially cylindrical, closed vessel which defines a space, and providing a horizontal support wall disposed adjacent an upper portion of the space.
- a plurality of tubes are affixed to the support wall and hang downwardly therefrom.
- a tube plate is situated adjacent a lower portion of the space.
- the tube plate includes upper and lower walls spaced vertically apart to form a chamber therebetween.
- Metallic bellows are disposed around respective tubes. Each bellows extends between the tube and the tube plate. The bellows are compressible and expandable to accommodate thermal expansion and contraction of the tubes.
- FIG. 1A shows a schematic view of a conventional plant for the manufacture of carbon black, such has already been described above.
- FIG. 1B shows a heat exchanger according to the state of the art, such has already been described above.
- FIG. 2 shows a heat exchanger according to the state of the art, such has already been described above.
- FIG. 3 shows a heat exchanger tube passing through a tube plate according to this invention, in a first embodiment.
- FIG. 4 shows the same section as in FIG. 3 but in an another embodiment.
- FIG. 3 shows how the lower parts of heat exchanger tubes 13 pass through a double walled tube plate 18 A in the lower region of the heat exchanger.
- That known design has been changed in accordance with the present invention in such a way that the tubes 13 now hang from their upper portions instead of having their lower parts standing on a plate.
- the tubes 13 In order to hang the tubes from their upper portion they are simply welded at the point where they pass through a hole in a horizontal suspension wall 13 A which is located at the upper end of the heat exchanger, for example, located at the level of the step 23 in FIG. 1B and/or FIG. 2.
- the compensators 24 in those figures are replaced by simple welded joints W, whereby the tubes 13 hang down from the wall 13 A.
- the double-walled tube plate 18 A comprises upper and lower walls 19 A and 20 A.
- the upper wall 19 A and the lower wall 20 A of the tube plate 18 A are depicted.
- the upper wall 19 A comprises a ceramic insulation 25 and a wall 26 of iron or steel plate.
- the lower wall 20 A can comprise refractory ceramic compound 27 , an insulating ceramic compound 28 and a steel wall 29 .
- the refractory ceramic material 27 may be required in order to insulate the tube plate 18 A from heat radiation emitted by the combustion chamber 10 positioned therebeneath.
- the manifold 21 formed between the upper and lower walls 19 A, 20 A of the tube plate 18 A can be sub-divided into a number of channels by ribs in accordance with the Swedish patent application 9603739-5. This is, however, not an important characteristic of the present invention, which relates to the off-loading (i.e. eliminating the loading from) the tube plate.
- a protective tube or a so called ferrule 30 is provided in the lower part of the tube 13 for conducting the inflow of very hot gases. The ferrules function is to impede the aggressive gases from coming in contact with tube 13 plus, via insulation, to limit the absorption of heat by the tube plate.
- An intermediate insulation 31 made for example from ceramic blanketing, provides insulation between this ferrule 30 and tube 13 . In order to create space for this insulation 31 , the inner diameter of the ferrule is largest at its opposite ends and then gradually narrows to a smaller diameter.
- a fitting ring 42 is welded in place along the exterior of the upper end of the ferrule, partly for press fitting of the ferrule in the tube, and partly in order to secure the insulation 31 in place.
- a welding ring 43 is provided next to the lower end of the tube.
- a protecting sleeve 32 is provided outside the tube 13 , and a further insulation 33 , preferably a ceramic blanket, is provided between the protective sleeve 32 and the tube 13 .
- the protecting sleeve 32 is welded at its lower foot to the tube 13 , while at the top it quite simply rests against the tube 13 .
- the insulation 33 is thereby enclosed.
- a conical part 34 is welded to the outside of the protective sleeve 32 , the said part 34 transforming into a cylindrical part 35 which has a larger diameter than that of the protective sleeve 32 .
- an outer sleeve 37 is provided.
- This outer sleeve 37 is fixed, at its top, in the wall of the upper support 26 and is welded to the steel wall 29 at a distance above its bottom edge.
- An end cap 38 is fastened to the lower edge of the outer sleeve 37 .
- This end cap 38 can have a number of outwardly projecting flaps, for example three in total, which are bent up and over the lower edge of the outer sleeve 37 and then welded to the outside of the outer sleeve, while the end cap 38 otherwise only lies in abutment against the lower edge of the outer sleeve.
- a locking ring 36 with a mainly L-shaped cross section is welded in proximity to the lower part of the interior of the outer sleeve 37 .
- the ring shaped space which is defined by the locking ring 36 , protective sleeve 32 , the outer sleeve 37 and the end cap 38 is occupied by one or two sealing rings 39 a , 39 b .
- These sealing rings can be made of ceramic blanketing, ceramic rope or such like.
- a compensating bellows 40 is provided in the cylindrical chamber formed between the protective sleeve 32 and the outer sleeve 37 , which bellows is welded gas-tight at its top in the transition area between the conical part 34 and the upper cylindrical end part 35 of the protective sleeve. At its foot, the bellows is gas-tight welded to the locking ring 36 . Because the bellows can retract and expand, the tube 13 is allowed to expand and contract because of variations in the temperature. In the situation illustrated in FIG. 3, the cylindrical upper end part of the sleeve 32 abuts against the upper tube plate wall 26 , so the tube 13 will exhibit a relatively lower temperature. In a modified arrangement illustrated in FIG. 4, the protective upper cylindrical end part of the sleeve 32 is distanced from the wall 26 , so the tube 13 will exhibit a relatively higher temperature compared with the situation in FIG. 3.
Abstract
Description
- This is a continuation-in-part of International Application Serial No. PCT/SE98/00952, filed May 20, 1998 and which designated the United States.
- The present invention relates to a tube heat exchanger and a tube plate for supporting the tubes of a tube heat exchanger. Specifically the invention relates to a heat exchanger with vertical tubes of considerable lengths having weights which in combination with high temperature subject the tubes themselves and the tube plate to considerable stresses. This tube plate is particularly suitable for use in tube heat exchangers which produce carbon black.
- Carbon black is the term used for the finely divided powder forms of carbon which are produced by incomplete combustion or thermic degradation of natural gas or mineral oil. Depending on the method of production, different types of carbon black arise, namely so called channel black, furnace black and pyrolysis black (also called thermal black). Furnace black is by far the most important form of carbon black and is used to a considerably larger extent than the other two. The present invention relates specifically to this type of carbon black, which in the present application is referred to simply as just “carbon black”.
- FIG. 1A illustrates a conventional plant for the production of carbon black (i.e. of the furnace black type). Incoming combustion air flows through a tube conduit1 into the upper part of a
tube heat exchanger 2, in which it is preheated before supporting the subsequent combustion of oil in the burner 9 and thecombustion reactor 3. The thus preheated air is passed into thecombustion chamber 10 via aconduit 5. Oil is added to said reactor via atube conduit 4. The amount of air corresponds to about 50% of the stoichiometric amount of oxygen gas required for a complete combustion of the oil, whereby carbon black is formed. It is also possible to add water into thereactor 3, which has an impact on the quality of the final product. The mixture of the suspended carbon black in the consumed combustion air is led away from the top of the heat exchanger via a conduit 6, through a cooler 7 which is normally water cooled to afilter arrangement 8, conventionally equipped with textile bag filters. In this filter arrangement the carbon black is filtered off from the gas flow, which is then passed out through anon-return valve 16 for further purification in aplant 11, before it is exhausted into the ambient air via achimney 12. - The construction of the
conventional heat exchanger 2 may be more clearly seen in FIG. 1B. The heat exchanger is of the tube type, with a plurality of substantiallyvertical tubes 13 whose lower ends are supported on a tube plate 5A. The gases from the combustion process rise up the insides of these tubes, whereby they are cooled by the air that enters via the inlet 1 and passes outside thetubes 13 downwards towards theoutlet 5, in the space enclosed by theouter jacket wall 14. In order to increase heat transfer, the air coming through the inlet 1 is subjected to a reciprocal movement by an arrangement of a plurality of mainlyhorizontal baffles 15. These are made of plates which extend across about ¾ of the diameter of the heat exchanger whereby each plate is provided with a plurality of holes for the receipt of thetubes 13. The temperature at the inlet 1 of theheat exchanger tubes 13 may be about 1000° and the air coming through conduit 1 may be heated to about 800°. These conditions result in utmost severe stresses for the materials in the heat exchanger. The part of the heat exchanger that is submitted to the highest mechanical stress is the lower part of the jacket and the tube plate 5A where the temperature may amount to 900°. Thus, with an internal pressure of approximately 1 bar at that temperature, a jacket wall diameter of about 2000 mm, tubes numbering between 50 and 150, plus a height of the tower of approximately 13 m, it can be easily understood that the tube plate must be able to withstand exceptionally large stresses, particularly since thetubes 13 rest with their entire weight on the tube plate. Furthermore, even the lower portions of theactual tubes 13 are exposed to heavy loads via their own weight in combination with the high temperatures. Thetubes 13 have individual compensator devices placed at the top of each tube, the function of which is to off-load the thermally induced stresses in the tubes, as a result, for example of clogging. - An equivalent problem involving the actual
outer jacket wall 14 has been solved as described in commonly-assigned Swedish Patent Application No. 9504344-4, corresponding to U.S. Pat. No. 5,866,083, the contents of which are hereby incorporated by reference. According to the invention, the heat exchanger includes a further jacket wall, which is substantially cylindrical and is placed inwards and mainly concentrically to the outer jacket wall so that at both ends open, mainly cylindrical spaces are formed in the gap between the two jacket walls, whereby the gas which flows in through the inlet passes through this space before coming into contact with the tubes of the heat exchanger. Occasionally the tube plate has failed to stand up to the heavy loads to which it has been exposed leading to very high repair costs. - Attempts have been made to cool the lower tube plate through a double bottom construction as shown in FIG. 2. In this design, a portion of the incoming air which enters through the inlet1 is lead away in a
vertical pipe 17 and flows down into a double-wall tube plate 18, which includes an upper thermally insulatedwall 19 and a lower thermally insulatedwall 20, so that a chamber (manifold) 21 is formed between the two walls. Air from thevertical pipe 17 flows into themanifold 21 and hence cools the tube plate, after which the air flows out through anexhaust pipe 22 and is returned to the heat exchanger. However this design has not proved to be sufficiently effective since it does not cool the tube plate adequately. Therefore it has been proposed that, in accordance with Swedish Patent Application 9603739-5, themanifold 21 be split up into a number of channels through the use of dividing walls, whereby each channel is provided with an inlet and an exhaust, and a number of heat exchange tubes pass through each channel. This has solved the problem of excessive temperatures in the base plate in a satisfactory manner, but the lower portions of the heat exchanger tubes are still very hot and can, for example, bend or buckle. It should be borne in mind that a 13 m long heat exchanger tube can weigh approximately 100 kg. Since the tube stands with its entire weight on the tube plate, the tube plate and the lower, very hot parts of the tubes are particularly heavily loaded. When a buckle is induced, stress on the tubes increases and the deformation process can accelerate. - A prime objective of the present invention is thus to produce a heat exchanger in which the lower parts of the tubes are protected from large loads.
- A second objective of the invention in question is even to protect the lower tube plate from large loads.
- These and other objectives have been successfully achieved in a surprisingly simple manner by designing the heat exchanger so as to include a substantially cylindrical, closed vessel which defines a space, and providing a horizontal support wall disposed adjacent an upper portion of the space. A plurality of tubes are affixed to the support wall and hang downwardly therefrom. A tube plate is situated adjacent a lower portion of the space. The tube plate includes upper and lower walls spaced vertically apart to form a chamber therebetween. Metallic bellows are disposed around respective tubes. Each bellows extends between the tube and the tube plate. The bellows are compressible and expandable to accommodate thermal expansion and contraction of the tubes.
- For illustrative but non-limiting purposes, preferred embodiments of the invention will now be described with reference to the appended drawings, in which:
- FIG. 1A shows a schematic view of a conventional plant for the manufacture of carbon black, such has already been described above.
- FIG. 1B shows a heat exchanger according to the state of the art, such has already been described above.
- FIG. 2 shows a heat exchanger according to the state of the art, such has already been described above.
- FIG. 3 shows a heat exchanger tube passing through a tube plate according to this invention, in a first embodiment.
- FIG. 4 shows the same section as in FIG. 3 but in an another embodiment.
- FIG. 3 shows how the lower parts of
heat exchanger tubes 13 pass through a double walled tube plate 18A in the lower region of the heat exchanger. - Such an arrangement would be employed in lieu of an arrangement disclosed in Swedish Patent Applications 9504344-4 and 9603739-5 which were discussed earlier in connection with FIGS.1-2, wherein the feet of the
heat exchanger tubes 13 were securely welded to a tube plate, and upper parts of the tubes extended in collars or compensators disposed at the upper end of the heat exchanger, in order to permit thermal expansions or contractions of the tubes. - That known design has been changed in accordance with the present invention in such a way that the
tubes 13 now hang from their upper portions instead of having their lower parts standing on a plate. In order to hang the tubes from their upper portion they are simply welded at the point where they pass through a hole in ahorizontal suspension wall 13A which is located at the upper end of the heat exchanger, for example, located at the level of thestep 23 in FIG. 1B and/or FIG. 2. Thecompensators 24 in those figures are replaced by simple welded joints W, whereby thetubes 13 hang down from thewall 13A. - The double-walled tube plate18A comprises upper and
lower walls 19A and 20A. In FIG. 3 theupper wall 19A and the lower wall 20A of the tube plate 18A are depicted. Theupper wall 19A comprises a ceramic insulation 25 and awall 26 of iron or steel plate. The lower wall 20A can comprise refractory ceramic compound 27, an insulating ceramic compound 28 and asteel wall 29. The refractory ceramic material 27 may be required in order to insulate the tube plate 18A from heat radiation emitted by thecombustion chamber 10 positioned therebeneath. - The manifold21 formed between the upper and
lower walls 19A, 20A of the tube plate 18A can be sub-divided into a number of channels by ribs in accordance with the Swedish patent application 9603739-5. This is, however, not an important characteristic of the present invention, which relates to the off-loading (i.e. eliminating the loading from) the tube plate. A protective tube or a so calledferrule 30 is provided in the lower part of thetube 13 for conducting the inflow of very hot gases. The ferrules function is to impede the aggressive gases from coming in contact withtube 13 plus, via insulation, to limit the absorption of heat by the tube plate. Anintermediate insulation 31, made for example from ceramic blanketing, provides insulation between thisferrule 30 andtube 13. In order to create space for thisinsulation 31, the inner diameter of the ferrule is largest at its opposite ends and then gradually narrows to a smaller diameter. - A fitting ring42 is welded in place along the exterior of the upper end of the ferrule, partly for press fitting of the ferrule in the tube, and partly in order to secure the
insulation 31 in place. In order to facilitate welding offerrule 30 intube 13, awelding ring 43 is provided next to the lower end of the tube. Furthermore a protectingsleeve 32 is provided outside thetube 13, and a further insulation 33, preferably a ceramic blanket, is provided between theprotective sleeve 32 and thetube 13. The protectingsleeve 32 is welded at its lower foot to thetube 13, while at the top it quite simply rests against thetube 13. The insulation 33 is thereby enclosed. At the top of the sleeve, a conical part 34 is welded to the outside of theprotective sleeve 32, the said part 34 transforming into acylindrical part 35 which has a larger diameter than that of theprotective sleeve 32. Radially outside theprotective sleeve 32, and substantially concentric to it, anouter sleeve 37 is provided. - This
outer sleeve 37 is fixed, at its top, in the wall of theupper support 26 and is welded to thesteel wall 29 at a distance above its bottom edge. Anend cap 38 is fastened to the lower edge of theouter sleeve 37. Thisend cap 38 can have a number of outwardly projecting flaps, for example three in total, which are bent up and over the lower edge of theouter sleeve 37 and then welded to the outside of the outer sleeve, while theend cap 38 otherwise only lies in abutment against the lower edge of the outer sleeve. - A locking
ring 36, with a mainly L-shaped cross section is welded in proximity to the lower part of the interior of theouter sleeve 37. The ring shaped space which is defined by the lockingring 36,protective sleeve 32, theouter sleeve 37 and theend cap 38 is occupied by one or two sealing rings 39 a, 39 b. These sealing rings can be made of ceramic blanketing, ceramic rope or such like. - A compensating bellows40 is provided in the cylindrical chamber formed between the
protective sleeve 32 and theouter sleeve 37, which bellows is welded gas-tight at its top in the transition area between the conical part 34 and the uppercylindrical end part 35 of the protective sleeve. At its foot, the bellows is gas-tight welded to the lockingring 36. Because the bellows can retract and expand, thetube 13 is allowed to expand and contract because of variations in the temperature. In the situation illustrated in FIG. 3, the cylindrical upper end part of thesleeve 32 abuts against the uppertube plate wall 26, so thetube 13 will exhibit a relatively lower temperature. In a modified arrangement illustrated in FIG. 4, the protective upper cylindrical end part of thesleeve 32 is distanced from thewall 26, so thetube 13 will exhibit a relatively higher temperature compared with the situation in FIG. 3. - By suspending the heat exchanger tubes from the
support wall 13A, the risk that the tubes will bend or deform because of the load from the weight of the tubes themselves is eliminated. As a result of the design of the bellows described in FIGS. 3 and 4, the pipes can thermally expand and contract freely. Bearing in mind that the tubes are often 13-15 m long, it can be easily understood that these expansions and contractions can be very significant and can be on the order of up to 5 cm. - An additional advantage has also been achieved as a result of this invention. In conventional heat exchangers wherein the tubes stand on a tube plate, it has been necessary to provide the tubes with greater wall thicknesses at their lower region, in order to increase the resistance to bending and buckling. Thus for example a 13 m long tube has been manufactured with 3 mm wall thickness in the upper 9 m extent, and 5 mm thick walls in the lower 4 m extent. Because of the invention described herein, it is possible to dispense with the lower, thicker wall thickness and hence the tube can be manufactured with for example 3 mm wall thickness along its entire length.
- Although the present invention has been described in connection with preferred embodiments thereof, it will be appreciated by those skilled in the art that additions, deletions, modifications, and substitutions not specifically described may be made without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (5)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE9701998-8 | 1997-05-28 | ||
SE9701998A SE511440C2 (en) | 1997-05-28 | 1997-05-28 | Heat exchanger with tubes hanging down in a double-walled, cooled and bellows tube plate, and tube plate for tube heat exchanger |
SE9701998 | 1997-05-28 | ||
PCT/SE1998/000952 WO1998054529A1 (en) | 1997-05-28 | 1998-05-20 | Heat exchanger with tubes suspended into a lower end plate allowing thermal movement; and end plate therefor |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/SE1998/000952 Continuation-In-Part WO1998054529A1 (en) | 1997-05-28 | 1998-05-20 | Heat exchanger with tubes suspended into a lower end plate allowing thermal movement; and end plate therefor |
Publications (2)
Publication Number | Publication Date |
---|---|
US20010042613A1 true US20010042613A1 (en) | 2001-11-22 |
US6334482B2 US6334482B2 (en) | 2002-01-01 |
Family
ID=20407120
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/449,522 Expired - Fee Related US6334482B2 (en) | 1997-05-28 | 1999-11-29 | Heat exchanger with tubes suspended into a lower end plate allowing thermal movement of the tubes |
Country Status (10)
Country | Link |
---|---|
US (1) | US6334482B2 (en) |
EP (1) | EP0985124B1 (en) |
JP (1) | JP2002500749A (en) |
CN (1) | CN1186584C (en) |
AU (1) | AU747857B2 (en) |
BR (1) | BR9808813A (en) |
CA (1) | CA2289855A1 (en) |
DE (1) | DE69806931T2 (en) |
SE (1) | SE511440C2 (en) |
WO (1) | WO1998054529A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
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US20050224213A1 (en) * | 2002-03-15 | 2005-10-13 | Behr Gmbh & Co. Kg | Heat exchanger |
US20080041563A1 (en) * | 2003-09-08 | 2008-02-21 | Graham Robert G | Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers |
US20090107660A1 (en) * | 2004-11-29 | 2009-04-30 | Ulf Eriksson | Pre-Heater For An Apparatus For The Production Of Carbon Black |
EP2331900A1 (en) * | 2008-09-22 | 2011-06-15 | AB K A Ekström&Son | Heat exchanger adapted for the production of carbon black |
US20150159956A1 (en) * | 2013-12-09 | 2015-06-11 | Balcke-Dürr GmbH | Tube Bundle Heat Exchanger Having Straight-Tube Configuration, Process Gas Cooler, Cooler For Gas Turbine Cooling Air, Gas Turbine Or Gas And Steam Turbine Power Plant, And Method For The Cooling Of Cooling Air |
KR20180063659A (en) * | 2016-12-02 | 2018-06-12 | 비에이치아이 주식회사 | Tube sealing structure of platen super header |
CN113267076A (en) * | 2021-06-04 | 2021-08-17 | 四川能投建工集团设计研究院有限公司 | Hydrocyanic acid oxidation reactor and tube plate cooling structure thereof |
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US7117934B2 (en) * | 2002-03-15 | 2006-10-10 | H2Gen Innovations, Inc. | Method and apparatus for minimizing adverse effects of thermal expansion in a heat exchange reactor |
DE102006016622B4 (en) * | 2006-04-06 | 2009-10-01 | Coperion Gmbh | Device for controlling the temperature of bulk material |
US9091510B2 (en) | 2007-03-21 | 2015-07-28 | Schott Corporation | Transparent armor system and method of manufacture |
AU2008327543B2 (en) * | 2007-11-21 | 2012-05-31 | The Petroleum Oil And Gas Corporation Of South Africa (Pty) Ltd | Tube sheet assembly |
US8752615B2 (en) * | 2008-01-08 | 2014-06-17 | General Electric Company | Methods and systems for controlling temperature in a vessel |
SE537215C2 (en) | 2012-02-13 | 2015-03-03 | Aktiebolaget Ka Ekstroems & Son | Heat exchanger adapted for the production of carbon black |
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CN106197127B (en) * | 2016-08-31 | 2019-06-07 | 浙江格尔泰斯环保特材科技股份有限公司 | A kind of bottom plate of tubular type gas-gas heat exchanger |
CN106197126B (en) * | 2016-08-31 | 2019-03-15 | 浙江格尔泰斯环保特材科技股份有限公司 | A kind of top plate of tubular type gas-gas heat exchanger |
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FR1178105A (en) * | 1957-07-02 | 1959-05-04 | Equip Thermiques Et De Recuper | Device for the individual expansion of tubes in a heat exchanger tube bundle and other applications |
US2989952A (en) * | 1957-12-23 | 1961-06-27 | Frederick W Richl | Combustion air preheater |
GB927573A (en) * | 1960-04-01 | 1963-05-29 | Exxon Research Engineering Co | Improved heat-exchange assembly |
FR1390942A (en) * | 1963-09-06 | 1965-03-05 | Fives Lille Cail | High performance fluid heater |
US3602296A (en) * | 1969-09-30 | 1971-08-31 | Thermal Transfer Corp | Metallic flue recuperators |
US3751228A (en) | 1970-12-16 | 1973-08-07 | V Semenov | Apparatus for reforming hydrocarbons under pressure |
FR2243386B1 (en) * | 1973-09-07 | 1976-11-19 | Commissariat Energie Atomique | |
US3992169A (en) | 1975-04-18 | 1976-11-16 | Cryogenic Technology, Inc. | Refrigerated cryogenic envelope |
US4360057A (en) * | 1979-06-18 | 1982-11-23 | Westinghouse Electric Corp. | High temperature abrasive resistant heat exchanger |
DE3027510A1 (en) | 1980-07-19 | 1982-02-18 | Hochtemperatur Reaktorbau Gmbh | DOME LID FOR CLOSING A VERTICAL EXCEPTION IN A PRESSURE VESSEL |
GB2147403B (en) | 1983-09-28 | 1987-05-07 | Nat Nuclear Corp Ltd | Tube-in-shell heat exchangers |
JPS60120196A (en) | 1983-12-01 | 1985-06-27 | Awaji Kakoki Kk | Tube type heat exchanger |
DE3676208D1 (en) | 1985-02-05 | 1991-01-31 | Asahi Glass Co Ltd | SEALING ARRANGEMENT FOR AN END PLATE AND A TUBE. |
FR2598496B1 (en) * | 1986-05-06 | 1990-01-05 | Stein Industrie | EXCHANGER FOR PRESSURE AIR HEATING IN COUNTER-CURRENT OF SMOKE FLOWING IN TUBULAR BEAMS |
US5079267A (en) | 1989-09-16 | 1992-01-07 | Xytel Technologies Partnership | Methanol production |
DE4404068C1 (en) * | 1994-02-09 | 1995-08-17 | Wolfgang Engelhardt | Heat exchanger |
SE506894C2 (en) | 1995-12-04 | 1998-02-23 | Edmeston Ab | Pipe heat exchanger with double-walled jacket and process and plant for the production of carbon black |
-
1997
- 1997-05-28 SE SE9701998A patent/SE511440C2/en not_active IP Right Cessation
-
1998
- 1998-05-20 WO PCT/SE1998/000952 patent/WO1998054529A1/en active IP Right Grant
- 1998-05-20 CN CNB988056070A patent/CN1186584C/en not_active Expired - Fee Related
- 1998-05-20 CA CA002289855A patent/CA2289855A1/en not_active Abandoned
- 1998-05-20 DE DE69806931T patent/DE69806931T2/en not_active Expired - Fee Related
- 1998-05-20 EP EP98924710A patent/EP0985124B1/en not_active Expired - Lifetime
- 1998-05-20 AU AU76813/98A patent/AU747857B2/en not_active Ceased
- 1998-05-20 JP JP50057099A patent/JP2002500749A/en not_active Ceased
- 1998-05-20 BR BR9808813-0A patent/BR9808813A/en not_active IP Right Cessation
-
1999
- 1999-11-29 US US09/449,522 patent/US6334482B2/en not_active Expired - Fee Related
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050224213A1 (en) * | 2002-03-15 | 2005-10-13 | Behr Gmbh & Co. Kg | Heat exchanger |
US20080041563A1 (en) * | 2003-09-08 | 2008-02-21 | Graham Robert G | Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers |
US7762317B2 (en) * | 2003-09-08 | 2010-07-27 | Heat Transfer International, Inc. | Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers |
US20090107660A1 (en) * | 2004-11-29 | 2009-04-30 | Ulf Eriksson | Pre-Heater For An Apparatus For The Production Of Carbon Black |
EP2331900A1 (en) * | 2008-09-22 | 2011-06-15 | AB K A Ekström&Son | Heat exchanger adapted for the production of carbon black |
EP2331900A4 (en) * | 2008-09-22 | 2013-02-20 | K A Ekstroem & Son Ab | Heat exchanger adapted for the production of carbon black |
US20150159956A1 (en) * | 2013-12-09 | 2015-06-11 | Balcke-Dürr GmbH | Tube Bundle Heat Exchanger Having Straight-Tube Configuration, Process Gas Cooler, Cooler For Gas Turbine Cooling Air, Gas Turbine Or Gas And Steam Turbine Power Plant, And Method For The Cooling Of Cooling Air |
US10006719B2 (en) * | 2013-12-09 | 2018-06-26 | Balcke-Durr Gmbh | Tube bundle heat exchanger having straight-tube configuration, process gas cooler, cooler for gas turbine cooling air, gas turbine or gas and steam turbine power plant, and method for the cooling of cooling air |
KR20180063659A (en) * | 2016-12-02 | 2018-06-12 | 비에이치아이 주식회사 | Tube sealing structure of platen super header |
CN113267076A (en) * | 2021-06-04 | 2021-08-17 | 四川能投建工集团设计研究院有限公司 | Hydrocyanic acid oxidation reactor and tube plate cooling structure thereof |
Also Published As
Publication number | Publication date |
---|---|
US6334482B2 (en) | 2002-01-01 |
AU747857B2 (en) | 2002-05-23 |
SE9701998D0 (en) | 1997-05-28 |
CA2289855A1 (en) | 1998-12-03 |
EP0985124A1 (en) | 2000-03-15 |
SE511440C2 (en) | 1999-09-27 |
JP2002500749A (en) | 2002-01-08 |
CN1258346A (en) | 2000-06-28 |
DE69806931D1 (en) | 2002-09-05 |
DE69806931T2 (en) | 2003-02-20 |
CN1186584C (en) | 2005-01-26 |
SE9701998L (en) | 1998-11-29 |
AU7681398A (en) | 1998-12-30 |
EP0985124B1 (en) | 2002-07-31 |
BR9808813A (en) | 2000-07-18 |
WO1998054529A1 (en) | 1998-12-03 |
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