EP0772010A1 - Réchauffeur d'air à brûleur - Google Patents

Réchauffeur d'air à brûleur Download PDF

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Publication number
EP0772010A1
EP0772010A1 EP96117521A EP96117521A EP0772010A1 EP 0772010 A1 EP0772010 A1 EP 0772010A1 EP 96117521 A EP96117521 A EP 96117521A EP 96117521 A EP96117521 A EP 96117521A EP 0772010 A1 EP0772010 A1 EP 0772010A1
Authority
EP
European Patent Office
Prior art keywords
air
combustion chamber
flow
partial
partial air
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.)
Granted
Application number
EP96117521A
Other languages
German (de)
English (en)
Other versions
EP0772010B1 (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
Original Assignee
Flucorrex AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 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 surface temperature is not limited to a maximum of 700 ° C can be ensured.
  • a good flow around the combustion chamber is essential because the flame in the combustion chamber has a temperature of over 1000 ° C and therefore wall temperatures of over 700 ° C can occur.
  • the object of the invention is to ensure intensive flue gas cooling in a single, compact device and, at the same time, to keep the surface temperature of all the outer surfaces coming into contact with the drying air as low as possible.
  • Effective cooling of both the flue gas generated in the combustion chamber in a flue gas heat exchanger and the outer surface of the combustion chamber can be achieved because drying air comes into contact with each of them, which has not yet been preheated in an upstream heat exchange step.
  • the greatest possible driving temperature gradient is available for cooling the outer surface of the combustion chamber, so that effective cooling of the outer surface is possible.
  • the second partial air flow of drying air to be heated flows along the outer surface of the combustion chamber, so that no areas with insufficient overflow that can overheat form, which can result in wall temperatures that are above the maximum tolerable.
  • the mass fraction of the second partial air stream is advantageously smaller than the mass fraction of the first partial air stream of air to be heated.
  • the mass fraction of the two partial air flows can be regulated in a simple and convenient manner, for example by adjusting the pressure loss of one or both partial air flows.
  • the combustion chamber is advantageously of essentially rotationally symmetrical shape and the main extent of the combustion chamber lies in the direction of the axis of rotation of the combustion chamber. Due to the rotationally symmetrical shape of the combustion chamber, the flow around it in the longitudinal direction, ie. H. relieved in the direction of the axis of rotation.
  • the second partial air stream of the drying air to be heated is preferably conducted in a closed flow channel which surrounds the combustion chamber, the closed flow channel having ribs or lamellae which are formed on the outer circumferential surface of the combustion chamber and extend in the main flow direction of the second partial air flow within the flow channel.
  • the provision of a closed flow channel and the ribs or fins arranged therein in the main flow direction ensure a controlled and uniform overflow of the outer surface of the combustion chamber. This will reduce the risk of uneven and locally insufficient overflow with the resulting local overheating avoided.
  • the heat-conducting fins applied to the air side that is to say the outer surface of the combustion chamber, result in a significant increase in the heat exchange surface, as a result of which the cooling effect is greatly improved. As a result, the volume flow of the second partial air flow can be reduced with the same heat transfer from the combustion chamber to the second partial air flow.
  • the flue gas heat exchanger preferably comprises a tube bundle in which the flue gases flow, the first partial air stream of the drying air to be heated being passed in a cross-countercurrent around the tube bundle.
  • the air heating system advantageously has an adjusting device for the mass flow ratio of the two partial air flows of the drying air to be heated.
  • the air heating system can be specifically adapted to different operating areas. If, for example, drying air of a higher or lower temperature is to be generated, this can be achieved by adjusting the mass flow ratio of the two partial air flows without causing undesired overheating within the air heating system.
  • the adjusting device is preferably an axially displaceable baffle plate.
  • the axially displaceable baffle plate narrows or widens the outlet cross section of the flow duct of one of the two partial air flows at the outlet from 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 stream of the drying air to be heated are conducted without mutual mixing and thus without the possibility of mutual pressure equalization in the air heating system.
  • the air heating system shown in Fig. 1 is generally designated by reference number 10.
  • the air heating system 10 has a suitable housing 12, the construction of which, with various housing covers, flanges and supporting components, enables both the safe installation of the air heating system 10 on the stand area 14 and good accessibility to the individual assemblies in order to maintain and possibly clean the air heating system 10 can.
  • An essential component of the air heating system 10 is the combustion chamber 16, which is firmly connected to a burner 18, which generates flue gases by burning a liquid or gaseous fuel.
  • the operation of the burner 18, the burner flame 19 of which is shown schematically in the figures, is not explained in more detail below, since this is a connection of a burner to a combustion chamber which is customary in the art.
  • the tubes of the tube bundle of the flue gas heat exchanger 22 are charged with the flue gases A and end in a flue gas outlet 24, from which the flue gases are removed in a suitable manner.
  • the flue gases are guided in a tube bundle loop and the flow direction of the flue gases on the one hand changed by a targeted bending of the individual tubes in the deflection area 25 and on the other hand by interposing a deflection bell 26.
  • the tube bundle of the flue gas heat exchanger 22 runs before leaving the air heating system 10 along an air inlet 28 through which a partial air flow of the air to be heated enters the air heating system 10.
  • the air which has not yet been preheated through the air inlet 28 is split into two partial air streams B and C which flow independently of one another through the air heating system 10 and are only mixed with one another after they have left the air heating system 10.
  • the two partial air streams can be separated in any way, for example by installing separating and air guiding elements which are arranged in the housing 12.
  • a wall of the deflection bell 26 of the flue gas heat exchanger 22 forms part of the separating elements required for this.
  • the first partial air flow B flows around the flue gas tube bundle of the flue gas heat exchanger 22.
  • Partial airflow B This creates a cross-countercurrent flow between the flue gas to be cooled and the partial airflow B to be heated of the air to be heated, whereby the best possible use of the primary fuel energy used in the burner is achieved.
  • the first partial air flow B after flowing around the tube bundles of the flue gas heat exchanger 22, leaves the air heating system 10 through outlet openings 30, to which suitable devices can be connected, in order to heat the first one emerging from the outlet openings 30 Record partial air flow B and continue to convey it as intended.
  • the second partial air flow C of the air to be heated is passed through the air heater completely separately from the first partial air flow B and is passed in a suitable manner, for example via air guide plates 32, to the combustion chamber 16, whereupon the second partial air flow C enters a chamber jacket 34, which the combustion chamber 16 surrounds.
  • the chamber jacket 34 is designed such that the second partial air flow C completely flows around the outer jacket surface of the combustion chamber 16.
  • ribs or fins 36 are preferably formed on the outer lateral surface of the combustion chamber 16. These fins 36 enlarge the heat-emitting surface of the combustion chamber 16 and thus increase the cooling effect by the second partial air flow C guided in the chamber jacket 34.
  • the dimensioning of the laminated combustion chamber size is based on the specification that the flue gases in the combustion chamber are cooled to such an extent that also on Combustion chamber outlet 20, at which the flue gases enter the tube bundle of the flue gas heat exchanger 22, the tube surface temperature does not exceed a temperature of 700 ° C.
  • the second partial air flow C is guided through the chamber jacket 34 parallel to the longitudinal axis of the preferably substantially cylindrical combustion chamber 16 and leaves the air heating system 10 at the end of the combustion chamber 16 remote from the burner.
  • the second partial air flow C is split into two partial flows on exiting the air heating system, a first partial flow leaving the air heating system essentially in the direction of the flow through the chamber jacket 34, but the other flow is deflected and the end, remote from the burner, preferably bell-shaped flows around the combustion chamber 16 before it leaves the air heating system.
  • baffle plate 38 which at the same time serves to set the mass flow ratio of the two partial air flows B and C of the air to be heated.
  • the baffle plate 38 in the axial direction, i. H. in the direction of the longitudinal axis of the substantially cylindrical combustion chamber 16, are shifted and fixed in position.
  • the displacement of 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 completely separated inside the air heating system 10 Flow guidance of the two partial air flows B and C, the pressure drop on the outlet side of the second partial air flow C affects the distribution of the two partial air flows at the air inlet 28. The more the outlet cross-section for the second partial air flow C is narrowed with the help of the baffle plate 38, the smaller the second partial air flow C becomes, because the pressure loss decreases as the flow velocity of the second partial air flow C decreases and the air to be dried is still present together at the air inlet 28, ie Pressure at air inlet 28 is the same for both partial air flows B and C.
  • the second partial air flow C is also taken up in a suitable manner and conveyed on as intended.
  • the dimensioning of the laminated combustion chamber size is according to the specification directs, after which the flue gases in the combustion chamber are cooled to such an extent that the pipe surface temperature does not exceed 700 ° C at the flue gas inlet into the tube bundle, can also be dimensioned smaller by the use of the likewise cold, second partial air flow C for cooling the combustion chamber 16 and thus the entire air heating system can be made more compact despite the optimal use of the primary fuel energy used.

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)
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 true EP0772010A1 (fr) 1997-05-07
EP0772010B1 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)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1076218A1 (fr) * 1999-08-11 2001-02-14 EISENMANN MASCHINENBAU KG (Komplementär: EISENMANN-Stiftung) Séchoir pour une installation de peinture
WO2002012812A1 (fr) * 2000-08-08 2002-02-14 Piovan S.P.A. Echangeur air/air particulierement destine a des dessiccateurs de plastiques granules pour moulage
EP1262726A1 (fr) * 2001-05-29 2002-12-04 Brückner Trockentechnik GmbH & Co. KG Dispositif de traitement de bandes continues textiles
GB2402465A (en) * 2003-05-27 2004-12-08 Edwin Robinson Split flow heat exchanger
CN103499193A (zh) * 2013-10-15 2014-01-08 李菊泉 干燥房专用热风炉
CN103884093A (zh) * 2012-12-20 2014-06-25 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
CN104006647A (zh) * 2014-06-11 2014-08-27 李雪奎 一种换热器
CN104359287A (zh) * 2014-11-07 2015-02-18 重庆汇田机械制造有限公司 内循环蚕茧烤房
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
DE102015008253A1 (de) 2015-06-26 2016-12-29 Eisenmann Se Wärmetauscher und Verfahren zum Betreiben eines Wärmtauschers
CN106319908A (zh) * 2015-06-16 2017-01-11 青岛海尔智能技术研发有限公司 干衣机
CN106679174A (zh) * 2016-12-29 2017-05-17 广州市祈雅典锅炉有限公司 高温热风炉
CN108645025A (zh) * 2018-05-14 2018-10-12 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

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10125960A1 (de) * 2001-05-29 2002-12-05 Brueckner Trockentechnik Gmbh Vorrichtung zur Behandlung von textilen Warenbahnen

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE2329305A1 (de) 1972-06-12 1974-01-03 Skoda Np Strahlungs-konvektions-lufterhitzer
DE3039065A1 (de) 1980-10-16 1982-05-13 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

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE2329305A1 (de) 1972-06-12 1974-01-03 Skoda Np Strahlungs-konvektions-lufterhitzer
DE3039065A1 (de) 1980-10-16 1982-05-13 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

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1076218A1 (fr) * 1999-08-11 2001-02-14 EISENMANN MASCHINENBAU KG (Komplementär: EISENMANN-Stiftung) Séchoir pour une installation de peinture
WO2002012812A1 (fr) * 2000-08-08 2002-02-14 Piovan S.P.A. Echangeur air/air particulierement destine a des dessiccateurs de plastiques granules pour moulage
EP1262726A1 (fr) * 2001-05-29 2002-12-04 Brückner Trockentechnik GmbH & Co. KG Dispositif de traitement de bandes continues textiles
GB2402465A (en) * 2003-05-27 2004-12-08 Edwin Robinson Split flow heat exchanger
GB2402465B (en) * 2003-05-27 2005-12-07 * Robinson Edwin A split-flow heat exchanger
CN103884093A (zh) * 2012-12-20 2014-06-25 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
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
CN103499193A (zh) * 2013-10-15 2014-01-08 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
CN104359287A (zh) * 2014-11-07 2015-02-18 重庆汇田机械制造有限公司 内循环蚕茧烤房
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
CN106319908A (zh) * 2015-06-16 2017-01-11 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
CN106679174A (zh) * 2016-12-29 2017-05-17 广州市祈雅典锅炉有限公司 高温热风炉
CN106679174B (zh) * 2016-12-29 2023-09-08 广东工业大学 高温热风炉
CN108645025A (zh) * 2018-05-14 2018-10-12 哈尔滨工业大学达通热能工程有限公司 燃煤气热风炉
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

Also Published As

Publication number Publication date
ATE201504T1 (de) 2001-06-15
DE19541035C1 (de) 1997-06-12
DK0772010T3 (da) 2001-07-30
EP0772010B1 (fr) 2001-05-23
ES2157384T3 (es) 2001-08-16

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