EP0772010B1 - Réchauffeur d'air à brûleur - Google Patents

Réchauffeur d'air à brûleur Download PDF

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Publication number
EP0772010B1
EP0772010B1 EP96117521A EP96117521A EP0772010B1 EP 0772010 B1 EP0772010 B1 EP 0772010B1 EP 96117521 A EP96117521 A EP 96117521A EP 96117521 A EP96117521 A EP 96117521A EP 0772010 B1 EP0772010 B1 EP 0772010B1
Authority
EP
European Patent Office
Prior art keywords
air
combustion chamber
branch stream
branch
heated
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96117521A
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German (de)
English (en)
Other versions
EP0772010A1 (fr
Inventor
Willi Frei
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Flucorrex AG
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Flucorrex AG
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Filing date
Publication date
Application filed by Flucorrex AG filed Critical Flucorrex AG
Publication of EP0772010A1 publication Critical patent/EP0772010A1/fr
Application granted granted Critical
Publication of EP0772010B1 publication Critical patent/EP0772010B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B21/00—Arrangements for supplying or controlling air or other gases for drying solid materials or objects
    • F26B21/001—Air generating units, e.g. movable or independent of drying enclosure
    • F26B21/002—Air generating units, e.g. movable or independent of drying enclosure with means for indirect air heating, i.e. using heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/06—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators
    • F24H3/08—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by tubes
    • F24H3/087—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by tubes using fluid fuel

Definitions

  • the invention relates to an air heating system for indirect heating of air for drying plants after the Preamble of claim 1 and a method for indirect heating of air for drying systems.
  • the first partial air flow flows across the combustion chamber, forms on the entry of the first partial air flow facing away from the combustion chamber with a lee area insufficient air movement on the lateral surface of the Combustion chamber, so that in this area a limitation of Surface temperature not to a maximum of 700 ° C can be ensured.
  • a good flow around the Combustion chamber is essential because the flame is in the Combustion chamber has a temperature above 1000 ° C and therefore Wall temperatures of over 700 ° C can occur.
  • FR-A-1.138.276 describes a burner whose exhaust gases be passed through a heat exchanger.
  • the combustion chamber is with helically arranged rib plates as well an outer jacket around the rib plates, so that a helical flow channel around the Combustion chamber forms around.
  • a first airflow to warming air hits the end of the helical Rib up and flow around the combustion chamber while a second Airflow of the air to be heated in counterflow to the Tubes of the heat exchanger is performed.
  • the invention lies in the The task is based on a single, compact device ensure intensive flue gas cooling and at the same time the surface temperature of all with the drying air in To keep the coming outer surfaces as small as possible.
  • Effective cooling both in the combustion chamber generated flue gas in a flue gas heat exchanger, as the outer surface of the combustion chamber can also be achieved because drying air is in contact with them occurs that has not yet been upstream Heat exchange step has been preheated. This stands for the cooling of the outer surface of the combustion chamber greatest possible driving temperature gradient available, so that an effective cooling of the outer surface is possible.
  • the second partial air stream to be heated Drying air along the outer surface of the Combustion chamber, so that there are no areas with insufficient Form overflow that can overheat, causing Wall temperatures can arise that are above the maximum tolerable lie.
  • the drying air to be heated without mutual Mixing can be performed in the air heating system in a simple and convenient way, for example by Adjust the pressure drop of one or both Partial air flows, the mass fraction of the two partial air flows be regulated
  • the air heating system has one Mass flow ratio adjusting device of the two Partial air flows of the drying air to be heated.
  • the air heating system can be targeted to different Operating areas to be adjusted. If, for example Drying air at a higher or lower temperature should be generated, this can be done by setting the Mass flow ratio of the two partial air flows reached be without causing unwanted overheating can come inside the air heating system.
  • the adjustment device is an axial one sliding baffle.
  • the axially movable Baffle plate narrows or widens the outlet cross section of the flow channel one of the two partial air flows on Leaves the air heating system and thus controls the Pressure loss of the respective partial air flow. This is possible because the first and the second partial air flow the drying air to be heated without mutual Mixing and thus without the possibility of one mutual pressure equalization in the air heating system be performed.
  • the mass fraction of the second is advantageous Partial airflow less than the mass fraction of the first Partial air flow in the air to be heated.
  • the combustion chamber is advantageously essentially the main extension is rotationally symmetrical the combustion chamber in the direction of the axis of rotation of the Combustion chamber. Due to the rotationally symmetrical shape of the Combustion chamber is flow around in the longitudinal direction, ie. H. in Direction of the axis of rotation easier.
  • the second partial air flow is preferably the warming drying air in a closed Flow channel guided, which surrounds the combustion chamber, wherein the closed flow channel ribs or fins has that on the outer surface of the combustion chamber are formed and in the main flow direction of the second Extend partial air flow within the flow channel.
  • the flue gas heat exchanger comprises Pipe bundle in which the flue gases flow, the first Partial air flow of the drying air to be heated in cross-counterflow is guided around the tube bundle.
  • the cross-countercurrent flow of the drying air to the flue gas the best possible use of those used in the burner Primary energy can be achieved by not yet preheated air in heat exchange with the outlet side End of the flue gas pipes is brought.
  • the air heating system shown in Fig. 1 is generally referred to by reference number 10.
  • the Air heating system 10 has a suitable housing 12, its construction with different housing covers, flanges and load-bearing components both ensure that the Air heating system 10 on the stand area 14 as well allows easy access to the individual components, wait for the air heating system 10 and if necessary to be able to clean.
  • An essential component of the air heating system 10 represents the combustion chamber 16 with a burner 18 connected by the combustion of a liquid or gaseous fuel produces flue gases.
  • the tubes of the tube bundle of the flue gas heat exchanger 22 are exposed to the flue gases A and end in one Flue gas outlet 24, from which the flue gases are suitable Way to be dissipated.
  • Flue gas outlet 24 from which the flue gases are suitable Way to be dissipated.
  • Example are the flue gases in a tube bundle loop led and the flow direction of the flue gases on the one hand through a specific bending of the individual pipes in the Deflection area 25 and on the other hand by interposing a deflection bell 26 changed.
  • the tube bundle of the flue gas heat exchanger 22 runs ahead the exit from the air heating system 10 along a Air inlet 28 through which a partial air flow to warming air enters the air heating system 10.
  • not yet preheated air is divided into two partial air flows B and C split up independently of each other by the Air heating system 10 flow and only after the outlet mixed together from the air heating system 10 become.
  • the separation of the two partial air flows can be reduced to one done in any way, for example by installation of separating and air guiding elements, which are in the housing 12 are arranged.
  • a wall of the deflection bell 26 of the Flue gas heat exchanger 22 is part of this required separating elements.
  • the first partial air flow B flows around the tube bundle of the Flue gas heat exchanger 22.
  • the first leaves Partial air flow B after flowing around the tube bundle Flue gas heat exchanger 22 through the air heating system 10 Exit openings 30 to which suitable facilities can connect to the from the outlet openings 30th emerging, heated first partial air stream B. and continue to transport them as intended.
  • the second partial air flow C of the air to be heated is completely separate from the first partial air flow B through the Air heater and is used in a suitable manner, for example via air guide plates 32 to the combustion chamber 16 passed, whereupon the second partial air flow C into one Chamber jacket 34 occurs, which surrounds the combustion chamber 16.
  • the chamber jacket 34 is designed so that the second Partial air flow C the outer surface of the combustion chamber 16 completely flows around.
  • Die Dimensioning of the laminated combustion chamber size is aimed according to the requirement that the flue gases in the Combustion chamber to be cooled down so far that Combustion chamber outlet 20, at which the flue gases enter the Pipe bundles of the flue gas heat exchanger 22 enter Pipe surface temperature not a temperature of 700 ° C exceeds.
  • the second partial air flow C is parallel to Longitudinal axis of the preferably substantially cylindrical formed combustion chamber 16 through the chamber jacket 34 performed and leaves the air heating system 10 on the end of the combustion chamber 16 remote from the burner.
  • the second partial air flow C is preferably at the outlet from the air heating system in two partial flows split, with a first substream Air heating system essentially in the direction of Flow through the chamber jacket 34 leaves, the other stream however, is deflected and the distant, preferably bell-shaped front end of the Combustion chamber 16 flows around before it reaches the air heating system leaves.
  • Moving the baffle plate 38 regulates the Flow resistance at the outlet of the second partial air flow C from the air heating system 10. Because of the inside the air heating system 10 completely separate Flow control of the two partial air streams B and C acts the outlet pressure loss of the second Partial air flow C on the distribution of the two Partial air flows at the air inlet 28. The stronger with help the baffle plate 38 the outlet cross section for the second Partial air flow C is narrowed, the smaller the second Partial air flow C, because the pressure drop with decreasing Flow velocity of the second partial air flow C decreases and the air to be dried still at the air inlet 28 exists together, d. H. the pressure at the air inlet 28 for both partial air flows B and C are the same size.
  • the Dimensioning of the laminated combustion chamber size directs what the flue gases in the combustion chamber so far be cooled that also at the flue gas inlet in the Tube bundle the tube surface temperature is not 700 ° C by using the also cold, second partial air flow C for cooling the combustion chamber 16 these are dimensioned smaller and thus the entire Air heating system despite the optimal use of the used primary fuel energy more compact become.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Drying Of Solid Materials (AREA)
  • Air Supply (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Direct Air Heating By Heater Or Combustion Gas (AREA)

Claims (9)

  1. Installation de chauffage d'air pour le réchauffement indirect d'air pour des installations de séchage, comportant
    un dispositif séparateur qui subdivise le courant d'air à réchauffer en deux courants d'air partiels, à savoir un premier courant d'air partiel (B) et un second courant d'air partiel (C) qui sont menés sans mélange mutuel à l'intérieur de l'installation de chauffage d'air,
    un échangeur de chaleur à gaz brûlés (22) qui amène les gaz brûlés
    (A) produits dans une chambre de combustion (16) en contact de transmission de chaleur avec l'air à réchauffer, l'échangeur de chaleur à gaz brûlés (22) étant alimenté en contre-courant croisé par le premier courant d'air partiel (B) qui n'est pas encore réchauffé, et
    une chambre de combustion (16) dont la surface enveloppe est entourée complètement et uniformément par le second courant d'air partiel (C) qui n'est pas encore réchauffé,
    caractérisée en ce que :
    l'installation de chauffage d'air possède un dispositif de réglage pour régler le rapport de débit de masse des deux courants d'air partiels, et
    le dispositif de réglage est une plaque à impact axialement mobile.
  2. Installation de chauffage d'air selon la revendication 1, caractérisée en ce que la chambre de combustion (16) est formée essentiellement à symétrie de révolution, et en ce que l'extension principale de la chambre de combustion se trouve en direction de l'axe de rotation de la chambre de combustion.
  3. Installation de chauffage d'air selon la revendication 2, caractérisée en ce que le second courant d'air partiel (C) entourant la chambre de combustion est mené en direction de l'axe de rotation de la chambre de combustion.
  4. Installation de chauffage d'air selon l'une quelconque des revendications précédentes, caractérisée en ce que le second courant d'air partiel (C) est mené dans un canal d'écoulement fermé (34) qui entoure la chambre de combustion (16).
  5. Installation de chauffage d'air selon la revendication 4, caractérisée en ce que le canal d'écoulement fermé comprend des nervures ou des lamelles (36) qui sont formées sur la surface enveloppe extérieure de la chambre de combustion et qui s'étendent dans la direction d'écoulement principal du second courant d'air partiel (C) à l'intérieur du canal d'écoulement (34).
  6. Installation de chauffage d'air selon l'une quelconque des revendications précédentes, caractérisée en ce que l'échangeur de chaleur à gaz brûlés (22) comprend un faisceau de tubes dans lequel s'écoulent des gaz brûlés (A).
  7. Procédé pour le réchauffement indirect d'air pour des installations de séchage, comprenant les étapes suivantes :
    on subdivise le courant d'air à réchauffer en deux courants d'air partiels, à savoir un premier courant d'air partiel et un second courant d'air partiel,
    on chauffe le premier courant d'air partiel qui n'est pas encore réchauffé par échange de chaleur au moyen d'un échangeur de chaleur à gaz brûlés, le premier courant d'air partiel étant mené en contre-courant croisé par rapport aux gaz brûlés chauds,
    on chauffe le second courant d'air partiel qui n'est pas encore réchauffé par échange de chaleur au moyen de la surface enveloppe d'une chambre de combustion, le second courant d'air partiel entourant complètement la chambre de combustion,
    on règle le rapport de débit de masse entre le premier courant d'air partiel et le second courant d'air partiel par modification de la perte de pression de l'un des deux courants d'air partiels que subit ce dernier lors de son passage à travers l'installation de chauffage d'air, et
    on extrait séparément le premier courant d'air partiel et le second courant d'air partiel hors de l'installation.
  8. Procédé pour le réchauffement de l'air dans une installation de chauffage d'air selon la revendication 7, caractérisé en ce que l'on mène le second courant d'air dans un canal d'écoulement entourant la chambre de combustion le long de lamelles qui dégagent la chaleur.
  9. Procédé pour le réchauffement de l'air dans une installation de chauffage d'air selon l'une ou l'autre des revendications 7 et 8,
    caractérisé en ce que l'on règle la proportion en masse d'air de séchage dans le second courant d'air partiel (C) plus petite que la proportion en masse d'air de séchage dans le premier courant d'air partiel (B).
EP96117521A 1995-11-03 1996-10-31 Réchauffeur d'air à brûleur Expired - Lifetime EP0772010B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19541035A DE19541035C1 (de) 1995-11-03 1995-11-03 Brennerbeheizter Lufterhitzer
DE19541035 1995-11-03

Publications (2)

Publication Number Publication Date
EP0772010A1 EP0772010A1 (fr) 1997-05-07
EP0772010B1 true EP0772010B1 (fr) 2001-05-23

Family

ID=7776560

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96117521A Expired - Lifetime EP0772010B1 (fr) 1995-11-03 1996-10-31 Réchauffeur d'air à brûleur

Country Status (5)

Country Link
EP (1) EP0772010B1 (fr)
AT (1) ATE201504T1 (fr)
DE (1) DE19541035C1 (fr)
DK (1) DK0772010T3 (fr)
ES (1) ES2157384T3 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19937901C2 (de) * 1999-08-11 2001-06-21 Eisenmann Kg Maschbau Trockner für eine Lackieranlage
IT249409Y1 (it) * 2000-08-08 2003-05-07 Piovan Spa Struttura di scambiatore aria-aria particolarmente per essicatoi di materia plastica in granuli per stampaggio.
EP1262726A1 (fr) * 2001-05-29 2002-12-04 Brückner Trockentechnik GmbH & Co. KG Dispositif de traitement de bandes continues textiles
DE10125960A1 (de) * 2001-05-29 2002-12-05 Brueckner Trockentechnik Gmbh Vorrichtung zur Behandlung von textilen Warenbahnen
GB2402465B (en) * 2003-05-27 2005-12-07 * Robinson Edwin A split-flow heat exchanger
CN103884093B (zh) * 2012-12-20 2016-02-24 岳阳远东节能设备有限公司 一种新型全钢结构直燃夹套式热风炉
CN103499193B (zh) * 2013-10-15 2015-04-01 李菊泉 干燥房专用热风炉
CN104006647A (zh) * 2014-06-11 2014-08-27 李雪奎 一种换热器
CN106319908B (zh) * 2015-06-16 2020-02-14 青岛海尔智能技术研发有限公司 干衣机
DE102015008253A1 (de) 2015-06-26 2016-12-29 Eisenmann Se Wärmetauscher und Verfahren zum Betreiben eines Wärmtauschers
CN105241212A (zh) * 2015-09-18 2016-01-13 广西节得乐生物质能源科技有限公司 一种生物质颗粒燃烧烘干设备
CN106679174B (zh) * 2016-12-29 2023-09-08 广东工业大学 高温热风炉
CN108645025B (zh) * 2018-05-14 2020-10-16 哈尔滨工业大学达通热能工程有限公司 燃煤气热风炉
CN112856813A (zh) * 2021-01-21 2021-05-28 济南宇弘热能设备有限公司 一种大型分体间接换热式燃气热风炉

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US2353606A (en) * 1941-04-23 1944-07-11 Watts Albert Edward Hot-air furnace
US2725051A (en) * 1953-01-06 1955-11-29 Delta Heating Corp Forced air recirculation floor furnace
US2737173A (en) * 1953-08-11 1956-03-06 Delta Heating Corp Combustion type unit heater
FR1138276A (fr) * 1955-03-22 1957-06-12 Générateur de fluide chaud
FR1353375A (fr) * 1963-04-11 1964-02-21 Breitenstein Gmbh J Réchauffeur d'air
CS159037B1 (fr) * 1972-06-12 1974-12-27
DE3039065C2 (de) * 1980-10-16 1984-05-24 Nordklima Lohner Klimatechnik GmbH, 2842 Lohne Warmluft-Heizvorrichtung
FR2522796A1 (fr) * 1982-03-05 1983-09-09 Sequipag Procede et installation perfectionnes pour le sechage de matieres en grains
DE3330924A1 (de) * 1983-08-27 1985-03-07 Hans Huras Gmbh, 6437 Kirchheim Waermetauscher
DE4308522A1 (de) * 1993-03-17 1994-09-22 Flucorrex Ag Flawil Lufterhitzungsanlage zur indirekten Erwärmung von Luft für Trocknungsanlagen

Also Published As

Publication number Publication date
EP0772010A1 (fr) 1997-05-07
ATE201504T1 (de) 2001-06-15
DE19541035C1 (de) 1997-06-12
DK0772010T3 (da) 2001-07-30
ES2157384T3 (es) 2001-08-16

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