DK174417B1 - heat exchanger - Google Patents
heat exchanger Download PDFInfo
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- DK174417B1 DK174417B1 DK198802599A DK259988A DK174417B1 DK 174417 B1 DK174417 B1 DK 174417B1 DK 198802599 A DK198802599 A DK 198802599A DK 259988 A DK259988 A DK 259988A DK 174417 B1 DK174417 B1 DK 174417B1
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- heat exchanger
- plate
- plates
- cams
- ridges
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
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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
- F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
- F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
- F28D19/041—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier with axial flow through the intermediate heat-transfer medium
- F28D19/042—Rotors; Assemblies of heat absorbing masses
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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
- F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
- F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
- F23L2900/00—Special arrangements for supplying or treating air or oxidant for combustion; Injecting inert gas, water or steam into the combustion chamber
- F23L2900/15021—Special arrangements for supplying or treating air or oxidant for combustion; Injecting inert gas, water or steam into the combustion chamber using regenerative heat exchanger bodies with different layers of material
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
DK 174417 B1 jDK 174417 B1 j
Den foreliggende opfindelse angår varmevekslere af den regenerative art.The present invention relates to regenerative heat exchangers.
En velkendt form for regenerativ varmeveksler er Ljungstrom typen, i hvilken et roterende element er stablet 5 med adskillige pakninger af i det væsentlige parallelle, adskilte varmeoverføringsplader, og to i det væsentlige halvcirkulaere områder af dette roterende element er adskilt i af såkaldte "sektorplader", og gassen, som skal opvarmes, fremføres sædvanligvis i én aksialretning gennem et af disse 10 halvcirkulære områder, og gassen, som skal afkøles, fremføres i den modsatte aksialretning gennem det andet halvcirkulære område, medens elementet drejes om sin akse.A well-known form of regenerative heat exchanger is the Ljungstrom type, in which a rotating element is stacked 5 with several packings of substantially parallel, separated heat transfer plates, and two substantially semicircular regions of this rotating element are separated by so-called "sector plates". and the gas to be heated is usually conveyed in one axial direction through one of these semicircular regions, and the gas to be cooled is conveyed in the opposite axial direction through the other semicircular region while the element is rotated about its axis.
Der er blevet foreslået forskellige former for plader til stabling i varmeveksleren.Various types of plates have been proposed for stacking in the heat exchanger.
15 Britisk patentskrift nr. 2 335 205 omhandler en særlig effektiv form for plader, ved hvilke en pakning af pladerne indbefatter over hinanden liggende, profilerede plader, som danner kanaler til varmevekslingsfluida. Hver plade indbefatter sammenhængende og parallelle kamme anbragt på hver 20 side af pladen, idet disse er adskilt af plane dele af en bredde større end højden af kammene betragtet fra pladens midterplan. Hver kam på den ene side af pladen er dannet grænsende til en kam på den anden side af pladen, så at kammene er anbragt på hver side af pladen dannende i det 25 væsentlige åbne S-formede dele set i tværsnit. Pladerne i pakningen er anbragt således, at kammene på én plade ligger på tværs af kammene på en tilgrænsende plade eller plader, så at tilgrænsende plader alene er i berøring med en anden ved punkter med mellemrum langs toppene af kammene. På denne 30 måde dannes kanaler, som indbefatter områder, der strækker sig ind i de åbne S-formede dele af kammene.British Patent Specification No. 2,335,205 discloses a particularly effective form of sheet, in which a pack of the sheets includes superposed, profiled sheets which form channels for heat exchange fluid. Each plate includes contiguous and parallel ridges disposed on each side of the plate, separated by planar portions of a width greater than the height of the ridges considered from the median plane of the plate. Each ridge on one side of the plate is formed adjacent a ridge on the other side of the plate so that the combs are disposed on each side of the plate forming substantially open S-shaped portions in cross section. The plates in the package are arranged such that the cams on one plate are transverse to the cams on one adjacent plate or plates, so that adjacent plates are only in contact with another at points at intervals along the tops of the cams. In this way, channels are formed which include areas extending into the open S-shaped portions of the ridges.
Det har vist sig, at der kan opnås en meget god varmeveksling med en sådan udformning, og selve pladerne kan fremstilles rimeligt økonomisk.It has been found that a very good heat exchange can be achieved with such a design and the plates themselves can be produced reasonably economically.
35 Ved brugen af denne art varmeveksler kan der imidler tid forekomme et forholdsvis stort trykfald hos gasserne, 2 DK 174417 B1 som strømmer derigennem. Gasserne bringes sædvanligvis til at strømme med blæsere, og hvis strømningsmodstanden gennem pakningerne af varmevekslerplader er stor, så forøges den energimængde, der kræves til at drive blæserne. Det kunne 5 være fordelagtigt at forøge anlæggets samlede virkningsgrad væsentligt.35 However, with the use of this type of heat exchanger, a relatively large pressure drop may occur in the gases, which flow through it. The gases are usually caused to flow with blowers, and if the flow resistance through the packings of heat exchanger plates is large, then the amount of energy required to drive the blowers is increased. It could be advantageous to significantly increase the overall efficiency of the plant.
Fra patentskrift GB 1 335 205 kendes ligeledes en varmeveksler med en opbygning som beskrevet i indledningen til krav 1, men her er formålet at løse et korrosionsproblem 10 i varmevekslerens kolde ende som følge af uens temperaturfordeling over kanalernes tværsnit. Det foreslås nu ifølge den foreliggende opfindelse at tilvejebringe en varmeveksler omfattende et roterende element og organer til selektivt at fremføre varme og kolde gasser gennem varmeveksleren for at 15 tilvejebringe en varm ende og en kold ende hos varmeveksleren, idet der er et antal bundter af varmevekslerelementer monteret i varmeveksleren, hvor hvert af bundterne indbefatter over hinanden anbragte, profilerede plader, der danner kanaler for varmevekslingsfluidaene, idet hver plade ind-20 befatter sammenhængende og parallelle kamme anbragt på hver side af pladen og adskilt af plane pladedele med en bredde større end højden af kammene betragtet fra et middelplan for pladen, hvor hver kam på den ene side af en plade er dannet grænsende til en kam på den anden side af pladen på 25 en sådan måde, at kammene anbragt på hver side af pladen danner i det væsentlige åbne S-formede dele set i tværsnit, og hvor pladerne i bundtet er anbragt sådan, at kammene på én plade ligger på tværs af kammene på mindst én tilgrænsende plade, så at tilgrænsende plader alene er i berøring med 30 hinanden ved punkter med mellemrum langs toppene af kammene og derved danner kanaler, som indbefatter områder, der strækker sig ind i de åbne S-formede dele af kammene, og hvor højden (N) af kammene og således mellemrummet mellem pladerne ved den kolde ende af varmeveksleren er væsentlig større 35 end ved den varme ende af varmeveksleren; især mellem 1,25 og 2 gange.Patent GB 1 335 205 also discloses a heat exchanger with a structure as described in the preamble of claim 1, but here the purpose is to solve a corrosion problem 10 in the cold end of the heat exchanger due to uneven temperature distribution over the cross sections of the ducts. It is now proposed according to the present invention to provide a heat exchanger comprising a rotary member and means for selectively conveying hot and cold gases through the heat exchanger to provide a hot end and a cold end of the heat exchanger, with a plurality of bundles of heat exchanger elements mounted. in the heat exchanger, each of the bundles including superposed, profiled plates forming channels for the heat exchange fluids, each plate including continuous and parallel ridges disposed on each side of the plate and separated by planar plate parts having a width greater than the height of the cams considered from a median plane of the plate, wherein each comb on one side of a plate is formed adjacent to a comb on the other side of the plate in such a way that the cams disposed on each side of the plate form substantially open S -shaped parts in cross-section and where the plates in the bundle are arranged such that the cams on one plate e lies transversely of the ridges on at least one adjacent plate, so that adjacent plates are in contact with each other alone at points at intervals along the tops of the ridges, thereby forming channels which include areas extending into the open S-shaped portions of the cams and wherein the height (N) of the cams and thus the space between the plates at the cold end of the heat exchanger is substantially greater than at the hot end of the heat exchanger; especially between 1.25 and 2 times.
3 DK 174417 B13 DK 174417 B1
Med en sådan udformning kan den samlede virkningsgrad forbedres væsentligt, fordi fluidets strømningsmodstand gennem kanalerne er væsentligt mindre ved den kolde ende af varmeveksleren end ved den varme ende. Det er fordelagtigt 5 at have tværsnitsdimensionerne af kanalerne, som er dannet mellem pladerne, forholdsvis små ved den varme ende og derved bevirke en væsentlig mængde turbulent strømning, idet dette giver anledning til en god varmeveksling ved de dele af varmeveksleren, som har varm og middel temperatur. Det har 10 imidlertid vist sig, at ved den kolde ende af varmeveksleren er varmevekslingsbehovet ikke så stort, og at turbulensen af strømningen ikke behøver at være så stor. Det har således uventet vist sig, at den samlede virkningsgrad kan forøges ved formindskelse af strømningsmodstanden ved den kolde 15 ende af varmeveksleren, og at man derved kan reducere den nødvendige energitilførsel til blæserne, som driver både de varme og kolde gasser.With such a design, the overall efficiency can be significantly improved because the flow resistance of the fluid through the ducts is substantially less at the cold end of the heat exchanger than at the hot end. It is advantageous to have the cross-sectional dimensions of the ducts formed between the plates relatively small at the hot end, thereby causing a substantial amount of turbulent flow, giving rise to a good heat exchange at those parts of the heat exchanger having hot and medium temperature. However, it has been found that at the cold end of the heat exchanger, the heat exchange need is not so great and that the turbulence of the flow need not be so great. Thus, it has been unexpectedly found that the overall efficiency can be increased by decreasing the flow resistance at the cold end of the heat exchanger, thereby reducing the necessary energy supply to the blowers which drive both the hot and cold gases.
Det er ligeledes muligt at forøge kanalernes tværsnit ved at forøge afstanden mellem kammene ved den kolde ende i 20 sammenligning med afstanden mellem kammene ved den varme ende af varmeveksleren.It is also possible to increase the cross-section of the ducts by increasing the distance between the cams at the cold end in comparison with the distance between the cams at the hot end of the heat exchanger.
Ved et særligt foretrukkent arrangement er forholdet mellem afstanden af kammene og højden af kammene på pladerne ved den kolde ende mellem 3,5 og 5,25.In a particularly preferred arrangement, the ratio of the distance of the cams to the height of the cams on the plates at the cold end is between 3.5 and 5.25.
25 Yderligere fordele kan opnås ved at ændre vinkelen af kammene på pladerne, så at der kan opnås en mere direkte gennemstrømning for gasserne. Det har f.eks. vist sig, når pladerne er i det væsentlige rektangulære i facon, at akserne for kammene ved den kolde ende fortrinsvis er vinkelstillet 30 til de to over for hinanden liggende, langsgående kanter af pladen under en vinkel på mellem 15 og 20°, medens akserne for kammene ved den varme ende befinder sig ved en noget større vinkel sædvanligvis mindst 20°. Dette kan frembringe den samme virkning som eller forøge virkningen af at have 35 tværsnittet af kanalen forøget ved den kolde ende.Further advantages can be obtained by changing the angle of the cams on the plates so that a more direct flow of the gases can be obtained. It has e.g. It is found that when the plates are substantially rectangular in shape that the axes of the cams at the cold end are preferably angled 30 to the two opposite longitudinal edges of the plate at an angle of between 15 and 20 °, while the axes of the cams at the hot end are at a somewhat larger angle, usually at least 20 °. This can produce the same effect as or increase the effect of having the cross-section of the duct increased at the cold end.
Ifølge en fordelagtig udførelsesform er der tilveje- 4 DK 174417 B1 bragt en pakning af varmevekslerplader til den kolde ende af en regenerativ varmeveksler hver indbefattende over hinanden anbragte, profilerede plader, som danner kanaler for varmevekslingsfluida, idet hver plade indbefatter sammen-5 hængende og parallelle kamme anbragt på hver side af pladen og adskilt af plane pladedele af en bredde, der er større end højden af kammene betragtet fra pladens midterplan, hvor hver kam på den ene side af pladen er dannet grænsende til en kam på den anden side af pladen på en sådan måde, at 10 kammene anbragt på hver side af pladen danner i det væsentlige åbne S-formede dele set i tværsnit, hvor pladerne i pakningen er anbragt således, at kammene på én plade ligger på tværs af kammene på mindst én tilgrænsende plade, så at tilgrænsende plader alene er i berøring med hinanden ved 15 punkter med mellemrum langs toppene af kammene og derved danner nævnte kanaler, som indbefatter områder, der strækker sig ind i de åbne S-formede dele af kammene, og hvor forholdet mellem afstanden mellem kammene og højden af kammene er mellem 3,5 og 5,25.According to an advantageous embodiment, a pack of heat exchanger plates is provided to the cold end of a regenerative heat exchanger each including superposed, profiled plates forming channels for heat exchange fluid, each plate including continuous and parallel. ridges disposed on each side of the plate and separated by planar plate portions of a width greater than the height of the ridges considered from the median plane of the plate, with each cam formed on one side of the plate adjacent to a comb on the other side of the plate of such that the 10 cams disposed on each side of the plate form substantially open S-shaped portions in cross section, the plates in the package being arranged such that the cams on one plate are transversely of the cams on at least one adjacent plate, so that adjacent plates are in contact with each other alone at 15 points at intervals along the tops of the ridges, thereby forming said channels, which includes areas extending into the open S-shaped portions of the ridges and wherein the ratio of the distance between the ridges and the height of the ridges is between 3.5 and 5.25.
20 Opfindelsen resulterer yderligere i en pakning af varmeoverføringsplader til den kolde ende af en regenerativ varmeveksler omfattende over hinanden anbragte, hovedsagelig rektangulære, profilerede plader, som danner kanaler for varmevekslingsfluidaene, idet hver plade indbefatter sam-25 menhængende og parallelle kamme anbragt på hver side af pladen og adskilt af plane pladedele af en bredde større end højden af kammene betragtet fra pladernes midterplan, hvor hver kam på den ene side af en plade er dannet grænsende til en kam på den anden side af pladen på en sådan måde, at 30 kammene anbragt på hver side af pladen danner i det væsentlige åbne S-formede dele set i tværsnit, idet pladerne i pakningen er anbragt således, at kammene på én plade ligger på tværs af kammene på mindst én tilgrænsende plade, så at tilgrænsende plader alene er i berøring med hinanden ved 35 punkter med mellemrum langs toppene af kammene og derved danner nævnte kanaler, som indbefatter og bryder ind i de 5 DK 174417 B1 åbne S-fortnede dele af kammene, og hvor akserne for kammene er vinkelstillet til to over for hinanden liggende langsgående kanter af pladerne under en vinkel på mellem 15 og ! 20°.The invention further results in a pack of heat transfer plates to the cold end of a regenerative heat exchanger comprising superposed, generally rectangular, profiled plates forming channels for the heat exchange fluids, each plate including interconnected and parallel cams disposed on each side of the the plate and separated by planar plate portions of a width greater than the height of the combs viewed from the median plane of the plates, each cam formed on one side of a plate adjacent to a comb on the other side of the plate in such a manner that the 30 combs are arranged on each side of the plate, substantially open S-shaped parts are seen in cross-section, the plates in the package being arranged such that the cams on one plate lie transversely of the cams on at least one adjacent plate, so that adjacent plates are in contact only with each other at 35 points at intervals along the tops of the ridges, thereby forming said channels which include and break into the open S-recessed portions of the cams, and the axes of the cams are angled to two opposite longitudinal edges of the plates at an angle of between 15 and 17 inches. 20 °.
5 Opfindelsen skal i det følgende beskrives nærmere ud fra udførelsesformer, idet der henvises til tegningen, på hvilken fig. 1 viser set ovenfra en varmeoverføringsplade til en pakning ifølge opfindelsen og til brug ved den varme 10 ende af en varmeveksler ifølge opfindelsen, fig. 2 et snit gennem pladen langs linien II-II i fig. 1, fig. 3 en perspektivgengivelse af to oven på hinanden anbragte varmevekslerplader som de i fig. 1 og 2 viste og 15 visende kanalsystemet i en pladepakning dannet af sådanne plader, fig. 4 på tilsvarende måde som fig. 1 en plade til en pladepakning ifølge opfindelsen til brug ved den kolde ende af varmeveksleren, og 20 fig. 5 på tilsvarende måde som fig. 2 den i fig. 4 viste plade.5 The invention will now be described in more detail from embodiments, with reference to the drawing, in which FIG. 1 is a plan view of a heat transfer plate for a gasket according to the invention and for use at the hot end of a heat exchanger according to the invention; FIG. 2 is a section through the plate along line II-II of FIG. 1, FIG. 3 is a perspective view of two heat exchanger plates arranged one on top of the other. 1 and 2 showing the duct system in a plate gasket formed by such plates; FIG. 4 in a manner similar to FIG. 1 shows a plate for a plate gasket according to the invention for use at the cold end of the heat exchanger; and FIG. 5 in a manner similar to FIG. 2 is the one shown in FIG. 4.
Den i fig. 1 viste plade 10 er dannet af metalplade med tilnærmelsesvis 0,5 mm's tykkelse, idet pladen er hovedsagelig rektangulær og har en af sine langsgående kanter 25 angivet ved 11. Pladen indbefatter plane dele 12 og parallelt foldede, sammenhængende kamme 14, som strækker sig under en vinkel α med den langsgående kant 11, idet denne vinkel ved den varme ende af varmeveksleren fortrinsvis er mindst 20°.The FIG. 1, plate 10 is formed of a metal plate of approximately 0.5 mm thickness, the plate being substantially rectangular and having one of its longitudinal edges 25 indicated by 11. The plate includes flat portions 12 and parallel folded continuous ridges 14 extending below an angle α with the longitudinal edge 11, this angle at the hot end of the heat exchanger being preferably at least 20 °.
Fig. 2 viser detaljeret tværsnittet af pladen langs 30 snitlinien II-II i fig. 1. Kammene 14 kan således ses at omfatte kamme 15 anbragt på hver side af pladen til dannelse af i det væsentlige S-formede dele set i tværsnit, idet de dobbelte kamme er indbyrdes forbundet med en vinkelstillet overkrydsningsdel 16.FIG. 2 shows in detail the cross-section of the plate along section line II-II of FIG. Thus, the ridges 14 can be seen to comprise ridges 15 disposed on each side of the plate to form substantially S-shaped portions seen in cross-section, the double ridges being interconnected with an angular crossover member 16.
35 Som det vil ses af fig. 3, hvor to identiske plader er stablet i forhold til hinanden, men i omvendt retning, 6 DK 174417 B1 er pladerne i pakningen anbragt således, at kammene på den ene plade ligger på tværs af kammene på den tilgrænsende plade eller de tilgrænsende plader, og de tilgrænsende plader er alene i berøring med hinanden ved punkter med mellemrum 5 langs toppene af kammene.35 As will be seen from FIG. 3, where two identical plates are stacked relative to each other, but in the opposite direction, the plates in the package are arranged such that the cams on one plate lie transversely of the cams on the adjoining plate (s), and the adjacent plates are in contact with each other only at points at intervals 5 along the tops of the ridges.
I fig. 2 er afstanden mellem kammene angivet ved henvisningsbetegnelsen P og højden fra kammene fra pladens midterplan er angivet som N. I pladerne i fig. 1, 2 og 3 er afstanden P 35 mm, og højden N er 5 mm, medens vinkelen a 10 er 2 0° .In FIG. 2, the distance between the cams is indicated by the reference numeral P and the height of the cams from the median plane of the plate is indicated as N. In the plates of FIG. 1, 2 and 3, the distance P is 35 mm and the height N is 5 mm, while the angle a 10 is 20 °.
I den i fig. 4 og 5 modificerede udformning af pladerne, som skal anvendes ved den kolde ende af pakningen, er afstanden igen 35 mm, men kamhøjden er 8,9 mm, og vinkelen a er mellem 15 og 20°. Dette arrangement sikrer, at tvær-15 snittet af kanalerne er næsten 80% større, og dette giver, sammen med at vinkelen a er mindre, anledning til en langt mindre strømningsmodstand for gas i kanalerne. I den specielle udformning, der er vist i fig. 1, 2 og 3 er forholdet P/N 7, medens forholdet P/N ved den i fig. 4 og 5 viste 20 opbygning er 3,93. En alternativ profil har afstanden P mellem 25 og 35 mm og højden N 6,8 mm, i hvilket tilfælde forholdet P/N er mellem 3,68 og 5,15. Det antages, at der opstår fordelagtige resultater, hvis forholdet P/N er mellem 3,5 og 5,25.In the embodiment shown in FIG. 4 and 5, modified designs of the plates to be used at the cold end of the gasket, the distance is again 35 mm, but the comb height is 8.9 mm and the angle a is between 15 and 20 °. This arrangement ensures that the cross-section of the ducts is almost 80% larger, and this, together with the angle a is smaller, gives rise to a much smaller gas resistance in the ducts. In the particular embodiment shown in FIG. 1, 2 and 3 are the ratio P / N 7, while the ratio P / N at the ratio shown in FIG. 4 and 5, the 20 structure is 3.93. An alternative profile has the distance P between 25 and 35 mm and the height N 6.8 mm, in which case the ratio P / N is between 3.68 and 5.15. It is assumed that favorable results will occur if the ratio P / N is between 3.5 and 5.25.
25 Pladerne ved den kolde ende er fortrinsvis af et tykkere materiale, f.eks. 0,8 mm i stedet for 0,5 mm, for at sætte disse plader i stand til at modstå de større belastninger og tilbøjeligheden til korrosion ved den kolde ende.The plates at the cold end are preferably of a thicker material, e.g. 0.8 mm instead of 0.5 mm, to enable these plates to withstand the greater stresses and the tendency to corrosion at the cold end.
F.eks. er der ved den kolde ende en større sandsynlighed 30 for kondensation og dannelsen af surhed, hvilket giver anledning til en højere grad af korrosion af pladerne ved den kolde ende, og det er derfor fordelagtigt, at disse plader gøres tykkere. Ligeledes er der ved den kolde ende en større sandsynlighed for tilsodning, og det har vist sig, at med 35 et større tværsnit af kanalerne og en mindre hældningsvinkel a lettes funktionen af en sodblæser i høj grad.Eg. For example, at the cold end there is a greater likelihood of condensation and the formation of acidity, which gives rise to a higher degree of corrosion of the plates at the cold end, and it is therefore advantageous for these plates to thicken. Likewise, at the cold end, there is a greater likelihood of seeding, and it has been found that with a larger cross-section of the channels and a smaller angle of inclination a, the function of a soot blower is greatly facilitated.
Claims (4)
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08622067A GB2183811A (en) | 1986-09-12 | 1986-09-12 | Rotary regenerative heat exchanger |
| GB8622067 | 1986-09-12 | ||
| SE8700396 | 1987-09-04 | ||
| PCT/SE1987/000396 WO1988002092A1 (en) | 1986-09-12 | 1987-09-04 | Heat exchangers |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| DK259988D0 DK259988D0 (en) | 1988-05-11 |
| DK259988A DK259988A (en) | 1988-05-11 |
| DK174417B1 true DK174417B1 (en) | 2003-02-17 |
Family
ID=10604126
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK198802599A DK174417B1 (en) | 1986-09-12 | 1988-05-11 | heat exchanger |
Country Status (9)
| Country | Link |
|---|---|
| JP (1) | JPH063357B2 (en) |
| KR (1) | KR960005790B1 (en) |
| CN (1) | CN1012591B (en) |
| AU (1) | AU598872B2 (en) |
| DK (1) | DK174417B1 (en) |
| ES (1) | ES2005317A6 (en) |
| GB (1) | GB2183811A (en) |
| IN (1) | IN171225B (en) |
| WO (1) | WO1988002092A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE455883B (en) * | 1987-02-27 | 1988-08-15 | Svenska Rotor Maskiner Ab | KIT OF TRANSFER TRANSFER PLATES, WHICH THE DOUBLE LOADERS OF THE PLATES HAVE A SPECIFIC INBOUND ORIENTATION |
| DE4122949A1 (en) * | 1991-07-11 | 1993-01-14 | Rothemuehle Brandt Kritzler | HEATING SHEET PACKAGE FOR REGENERATIVE HEAT EXCHANGER AND METHOD AND DEVICE FOR PRODUCING PROFILE SHEETS FOR SUCH HEATING SHEET PACKAGES |
| JP3450067B2 (en) * | 1993-12-07 | 2003-09-22 | 千代田化工建設株式会社 | Heat exchanger for combustion apparatus, regenerator for heat exchanger, and method for preheating oxidant for combustion |
| US5899261A (en) * | 1997-09-15 | 1999-05-04 | Abb Air Preheater, Inc. | Air preheater heat transfer surface |
| DE10221761A1 (en) * | 2002-05-16 | 2003-11-27 | Montz Gmbh Julius | Pack for heat and mass transfer |
| CN102878836A (en) * | 2011-10-28 | 2013-01-16 | 南通天华和睿科技创业有限公司 | Protecting device for radiator |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2872165A (en) * | 1954-09-04 | 1959-02-03 | Separator Ab | Plate type heat exchanger |
| BE567819A (en) * | 1958-04-08 | |||
| DE2007956A1 (en) * | 1970-02-20 | 1971-09-02 | Linde Ag | regenerator |
| GB1335205A (en) * | 1970-11-02 | 1973-10-24 | Svenska Rotor Maskiner Ab | Rotary regenerative heat exchangers |
| CH530608A (en) * | 1971-11-11 | 1972-11-15 | Steeb Dieter Chr | Circular heat exchanger for radial fans and process for its manufacture |
| CH530607A (en) * | 1971-11-11 | 1972-11-15 | Steeb Dieter Chr | Circular heat exchanger for radial fans and process for its manufacture |
| SE424143B (en) * | 1980-12-08 | 1982-07-05 | Alfa Laval Ab | Plate evaporator |
| US4396058A (en) * | 1981-11-23 | 1983-08-02 | The Air Preheater Company | Heat transfer element assembly |
-
1986
- 1986-09-12 GB GB08622067A patent/GB2183811A/en not_active Withdrawn
-
1987
- 1987-09-04 WO PCT/SE1987/000396 patent/WO1988002092A1/en unknown
- 1987-09-04 JP JP62505387A patent/JPH063357B2/en not_active Expired - Fee Related
- 1987-09-04 AU AU79136/87A patent/AU598872B2/en not_active Ceased
- 1987-09-04 KR KR1019880700529A patent/KR960005790B1/en not_active IP Right Cessation
- 1987-09-07 IN IN786/DEL/87A patent/IN171225B/en unknown
- 1987-09-10 CN CN87106287A patent/CN1012591B/en not_active Expired
- 1987-09-11 ES ES8702630A patent/ES2005317A6/en not_active Expired
-
1988
- 1988-05-11 DK DK198802599A patent/DK174417B1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| GB8622067D0 (en) | 1986-10-22 |
| KR960005790B1 (en) | 1996-05-01 |
| WO1988002092A1 (en) | 1988-03-24 |
| JPH01503800A (en) | 1989-12-21 |
| AU7913687A (en) | 1988-04-07 |
| DK259988D0 (en) | 1988-05-11 |
| CN1012591B (en) | 1991-05-08 |
| AU598872B2 (en) | 1990-07-05 |
| GB2183811A (en) | 1987-06-10 |
| KR880701857A (en) | 1988-11-05 |
| ES2005317A6 (en) | 1989-03-01 |
| CN87106287A (en) | 1988-05-04 |
| DK259988A (en) | 1988-05-11 |
| JPH063357B2 (en) | 1994-01-12 |
| IN171225B (en) | 1992-08-22 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PBP | Patent lapsed |
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