US20110011555A1 - Heat exchanger assembly for preheating comburent air for a glass furnace - Google Patents

Heat exchanger assembly for preheating comburent air for a glass furnace Download PDF

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Publication number
US20110011555A1
US20110011555A1 US12/864,049 US86404909A US2011011555A1 US 20110011555 A1 US20110011555 A1 US 20110011555A1 US 86404909 A US86404909 A US 86404909A US 2011011555 A1 US2011011555 A1 US 2011011555A1
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US
United States
Prior art keywords
heat exchanger
flue gas
air
assembly according
comburent
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.)
Abandoned
Application number
US12/864,049
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English (en)
Inventor
Alessandro Mola
Augusto Santero
Giampaolo Bruno
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.)
STARA GLASS SpA
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STARA GLASS SpA
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Filing date
Publication date
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Assigned to STARA GLASS S.P.A. reassignment STARA GLASS S.P.A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BRUNO, GIAMPAOLO, MOLA, ALESSANDRO, SANTERO, AUGUSTO
Publication of US20110011555A1 publication Critical patent/US20110011555A1/en
Abandoned legal-status Critical Current

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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
    • F28D17/00—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles
    • F28D17/02—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles using rigid bodies, e.g. of porous material
    • C—CHEMISTRY; METALLURGY
    • C03—GLASS; MINERAL OR SLAG WOOL
    • C03B—MANUFACTURE, SHAPING, OR SUPPLEMENTARY PROCESSES
    • C03B5/00—Melting in furnaces; Furnaces so far as specially adapted for glass manufacture
    • C03B5/16—Special features of the melting process; Auxiliary means specially adapted for glass-melting furnaces
    • C03B5/235—Heating the glass
    • C03B5/237—Regenerators or recuperators specially adapted for glass-melting furnaces
    • 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
    • F28D17/00—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles
    • F28D17/04—Distributing arrangements for the heat-exchange media
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P40/00—Technologies relating to the processing of minerals
    • Y02P40/50—Glass production, e.g. reusing waste heat during processing or shaping

Definitions

  • the present invention concerns a heat exchanger assembly for preheating comburent air for a glass furnace.
  • Continuous glass furnaces are known of that are fed with gaseous fuel or fuel oil, work at temperatures of around 1500-1600° C. and are equipped with heat exchangers for preheating comburent air by means of the heat contained in the flue gas leaving the furnace combustion chamber.
  • recuperative heat exchangers made of metal material.
  • the flow of comburent air is continuously piped directly into the furnace combustion chamber and is separated from the flow of flue gas by metal walls that exchange heat between the two flows.
  • the associated furnaces are known as “Unit Melters”. Given the technological limits regarding the heat resistance of metal, only the preheating of comburent air at temperatures below 800° C. is possible with these heat exchangers.
  • regenerative heat exchangers made of a refractory material which comprise a pair of regenerative chambers having respective upper openings that communicate with the furnace.
  • the associated furnaces are also called “chamber furnaces”.
  • the chambers, made of a refractory material can be located at the rear, for which the associated furnace is known as an “end-port” or “U-flame” furnace, or at the side, for which the associated furnace is known as a “sideport” furnace.
  • the flow of comburent air enters from a heat exchanger inlet, passes through one of the regeneration chambers and finally enters the furnace combustion chamber; the flue gas, instead, leaves the furnace combustion chamber, passes through the other regeneration chamber, where it surrenders thermal energy, and exits from a heat exchanger outlet.
  • a valve system is interposed between the two regeneration chambers, the air inlet and the flue gas outlet, and is controlled so as to swap the comburent airflow and the flue gas flow between the two regeneration chambers with cycles lasting a set time (typically around 20 minutes), so that the thermal energy accumulated in the regeneration chamber where the flue gas flows is transferred to the comburent air that flows through it during the next cycle.
  • the air is preheated to a temperature of 1200-1300° C., while the flue gas leaves the heat exchanger for porting to a chimney at a temperature of approximately 450-600° C.
  • known multi-chamber heat exchangers are of relatively large height and require significant occupied space below the ground level on which the furnace is built.
  • multi-chamber heat exchangers need so-called “washing” between each of the above-described cycles, i.e. it is necessary to wait for the air of the new cycle to evacuate the flue gas of the previous cycle from the regeneration chamber by driving it into the furnace.
  • the flame in the furnace's combustion chamber goes out for the entire duration of “washing”. Given the size of the chambers, in known plants the flame is out for approximately 30-40 seconds, which is a relatively long time.
  • the object of the present invention is to embody a heat exchanger assembly for preheating comburent air for a glass furnace that overcomes the above-specified drawbacks in a simple and economic manner.
  • a heat exchanger assembly for preheating comburent air for a glass furnace comprising:
  • FIG. 1 is a schematic plan view of a preferred embodiment of the heat exchanger assembly for preheating comburent air for a glass furnace according to the present invention
  • FIG. 2 is a section, with parts removed for clarity, made along line II-II of FIG. 1 ,
  • FIG. 3 is a diagram of a variant of the heat exchanger assembly in FIG. 1 .
  • FIG. 4 is similar to FIG. 1 and shows a detail of a further variant of the heat exchanger assembly in FIG. 1 .
  • reference numeral 1 indicates a heat exchanger assembly associated with a glass furnace 2 (partially shown), which is fed using fuel gas or fuel oil in the known manner and not described in detail.
  • the assembly 1 heats an airflow 3 , which enters through an inlet 4 at an ambient temperature of approximately 25° C.
  • the heat for heating the airflow 3 is supplied by a flow of flue gas 5 leaving the melting tank (not shown) of the glass furnace 2 .
  • the assembly 1 comprises a regenerative heat exchanger 10 , which in turn comprises:
  • Valves 19 a and 19 b are automatically controlled by a command and control unit 20 (shown schematically), according to a known strategy and not described in detail, for being switched together in a synchronized manner to swap the comburent airflow 18 and the flue gas flow 5 between the chambers 11 with cycles of set length (twenty minutes for example).
  • the valves 19 b on the ducts 15 comprise respective movable bulkheads or gates, which when in the closed position are in contact with the flue gas on one side and with the heated air on the other, and therefore tend to assume an intermediate temperature between that of the flue gas and that of the heated air. As this intermediate temperature would be too high for the metal material of the bulkheads, they are internally cooled by air, for example, external air taken in at ambient temperature.
  • each valve 19 b is substituted by a pair of valves.
  • the valves 44 and 45 of each pair comprise respective bulkheads or gates, which are jointly movable between the open and closed positions and face each other so as to define an air gap 46 when they are in the closed position.
  • the valves 44 are closer to the chambers 11 and are provided to ensure sealing. Instead, the gates of the valves 45 define respective shields in contact with the flue gas when in the closed position.
  • the air gap 46 defines a “cushion” that tends to keep valve 44 at a relatively low temperature and so protect the sealing of the valve 44 in the closed position.
  • the air gap 46 receives cooling air (for example air taken from the external environment) due to the effect of the depression naturally present in the air gap 46 when the valves 44 and 45 are closed.
  • this depression is approximately 120-160 Pa.
  • the gate of valve 45 is cooled on the opposite side of that exposed to contact with the flue gas, so as to protect metal material of the valve 45 from overheating.
  • the chambers 11 house respective sheets of heat accumulator elements 22 , of known type and not described in detail, which accumulate thermal energy during the cycle in which the corresponding camera 11 is traversed by the flow of flue gas 5 and release the accumulated thermal energy to the comburent airflow 18 that passes through this chamber 11 in the opposite direction during the successive cycle before entering the melting tank.
  • the assembly 1 also comprises a recuperative heat exchanger 25 made of metal material, operating continuously, that is without flow switching between flue gas and air, and positioned in series, upstream of the heat exchanger 10 when considering the direction of the comburent airflow 18 .
  • the heat exchanger comprises two passages 26 and 27 .
  • Passage 27 receives the flue gas flow 5 from an inlet 30 substantially coincident with outlet 14 and conveys the flue gas flow 5 to an outlet 31 that communicates with a chimney (not shown), preferably with a filtering system (not shown) interposed in between, to discharge the flue gas into the environment.
  • Passage 26 receives the airflow 3 from inlet 4 and conveys the airflow 3 to an outlet 28 that communicates with inlet 16 via a pipe 29 .
  • Two vertical sections of passage 26 are defined by respective air gaps, which are arranged coaxially around the respective vertical tubes of passage 27 , so as to make the air and flue gas run in counterflow and exchange thermal energy between the flue gas and the air through the metal walls that separate the passages 26 and 27 .
  • pipe 29 has a branch defined by a pipe 35 , thanks to which it is possible to bleed heated air 36 from the airflow 3 .
  • the heated air 36 is “clean”, i.e. it is conveyed in ducts separate from those for flue gas and can be used for various purposes.
  • the heated air 36 could be used for the district heating of buildings.
  • the heated air 36 could be used for preheating the fuel, such as natural gas for example, in a heat exchanger 36 a before feeding it to the glass furnace 2 , and/or for preheating the material that must be melted in the furnace 2 to make glass in a heat exchanger 36 b , (this material consists of raw materials or a mixture of raw materials and glass scrap to be recycled).
  • the flue gas produced by the furnace 2 is used for these types of preheating: instead, by using the heated air 36 , the special expedients that are indispensible for flue gas for sealing and keeping the ducts of the heat exchangers 36 a and 36 b in depression are not needed and, at the same time, fouling of these ducts is avoided.
  • the flow of heated air 36 bled off is controlled by a valve 37 (shown schematically) positioned on pipe 35 and controlled by the control unit 20 according to stored parameters and signals provided by sensors (not shown), such that the remaining comburent airflow 18 entering the heat exchanger 10 has the necessary theoretical flow rate for obtaining a given thermal power level and/or a given temperature and/or a given stoichiometrical ratio for the fuel inside the melting tank.
  • the flue gas has a temperature of approximately 1500° C. at the opening through which the flue gas leaves the melting tank, a temperature of approximately 1050° C. at outlet 14 (i.e. at inlet 30 ) and approximately 200° C. at outlet 31 , while the air has a temperature of approximately 750° C. at outlet 28 (i.e. at inlet 16 ) and approximately 1250° C. at the opening 12 through which the air enters the melting tank.
  • FIG. 3 shows a variant in which the constituent parts are only illustrated schematically and, where possible, are indicated by the same reference numerals as used in FIGS. 1 and 2 .
  • This variant basically differs from the embodiment in FIGS. 1 and 2 in that the heat exchanger 25 is substituted by a recuperative heat exchanger made of metal material comprising two stages 38 and 39 (shown schematically) positioned in series with respect to each other, and in that the assembly 1 comprises a branch 40 , in addition to branch 35 , for bleeding heated air from a duct 41 (shown schematically) that conveys the airflow 3 from stage 38 to stage 39 .
  • a branch 40 in addition to branch 35 , for bleeding heated air from a duct 41 (shown schematically) that conveys the airflow 3 from stage 38 to stage 39 .
  • hot and “clean” air i.e. not affected or fouled by any mixing with flue gas
  • stage 38 is defined by a counterflow heat exchanger, of a type similar to or different from the heat exchanger 25 shown in FIGS. 1 and 2 .
  • the flue gas has a temperature of approximately 440° C. between stages 38 and 39 , while in duct 41 and in branch 40 , the air has a temperature of approximately 130° C.
  • a reduction in these oxides could be performed using a technique known by the acronym SNCR (Selective Non-Catalytic Reduction), injecting a flow of ammonia, or a flow of 35-40% urea solution at outlet 14 through a channel 42 .
  • SNCR Selective Non-Catalytic Reduction
  • the assembly 1 allows the maximum possible temperature to be achieved for comburent air 18 entering the furnace 2 and obtains outgoing flue gas at a temperature of approximately 200° C.
  • energy losses and hence energy consumption are reduced with respect to heat exchangers that have outgoing flue gas with higher temperatures, while on the other it is possible to filter the outgoing flue gas using sleeve filtering systems.
  • part of the regenerative heat exchange used in known art is substituted by a recuperative type of heat exchange using metal material, which is simpler, is less expensive and is more flexible to run in response to changes in operating conditions. Due to the metal material with which it is constructed, the heat exchanger 25 is made to work with air that reaches a maximum temperature of 750-800° C., so as not to compromise the constructional characteristics of the metal material with which the heat exchanger 25 is made.
  • the heat exchanger 25 can be placed above the ground level 50 ( FIG. 2 ) on which the furnace 2 is installed, virtually eliminating the space occupied by the chambers 11 below ground level 50 .
  • the times needed for the so-called “washing” of the chambers 11 are also reduced. As mentioned above, these times are spent while swapping the flows between the chambers 11 and are tied to the need for “washing” flue gas from the chambers 11 by the passage of air before the chambers 11 are made to run regularly in the next cycle.
  • the “washing” and flame out times are also halved, without limiting the heat exchange of the assembly 1 , as there is the recuperative heat exchanger 25 .
  • the air 36 bled from branch 35 is in excess with respect to the necessary theoretical flow rate for obtaining a given thermal power level and/or a given temperature and/or a given stoichiometrical ratio in the furnace combustion chamber.
  • This excess air removes a greater quantity heat along the heat exchanger 25 with respect to the theoretical flow rate, and so protects the metal of the heat exchange walls from excessive temperatures and allows the heat exchanger 25 to be sized to heat the airflow 3 to a higher temperature with respect to that which could be reached with the theoretical air flow rate.
  • branch 35 possibly with branch 40 , allow a flow of hot and “clean” air to be obtained in a simple and efficient manner and to always achieve the correct thermal power level required from the furnace 2 .
  • recuperative heat exchanger made of metal material could have different constructional characteristics from those shown by way of example.
  • the pipes 17 could flow directly into the chambers 11 in parallel with the ducts 15 (as in FIG. 4 ).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Materials Engineering (AREA)
  • Organic Chemistry (AREA)
  • Dispersion Chemistry (AREA)
  • Air Supply (AREA)
  • Waste-Gas Treatment And Other Accessory Devices For Furnaces (AREA)
  • Gas Burners (AREA)
US12/864,049 2008-01-24 2009-01-23 Heat exchanger assembly for preheating comburent air for a glass furnace Abandoned US20110011555A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ITTO2008A000052 2008-01-24
IT000052A ITTO20080052A1 (it) 2008-01-24 2008-01-24 Gruppo scambiatore di calore per pre-riscaldare aria comburente per un forno da vetro
PCT/IB2009/000116 WO2009093134A2 (en) 2008-01-24 2009-01-23 Heat exchanger assembly for preheating comburent air for a glass furnace

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US20110011555A1 true US20110011555A1 (en) 2011-01-20

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US12/864,049 Abandoned US20110011555A1 (en) 2008-01-24 2009-01-23 Heat exchanger assembly for preheating comburent air for a glass furnace

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US (1) US20110011555A1 (it)
EP (1) EP2255143B1 (it)
ES (1) ES2668966T3 (it)
IT (1) ITTO20080052A1 (it)
PT (1) PT2255143T (it)
TR (1) TR201807066T4 (it)
WO (1) WO2009093134A2 (it)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102853702A (zh) * 2012-09-17 2013-01-02 扬州埃克森能源发展有限公司 一种工业烟气余热极限式回收利用方法
WO2013034541A1 (de) * 2011-09-06 2013-03-14 Software & Technologie Glas Gmbh (Stg) Verfahren zum betrieb eines regenerativ beheizten industrieofens und regenerativ geheizter industrieofen
ITTO20120974A1 (it) * 2012-11-08 2014-05-09 Stara Glass S P A Scambiatore di calore di tipo rigenerativo per un forno da vetro
WO2014110879A1 (zh) * 2013-01-18 2014-07-24 北京神雾环境能源科技集团股份有限公司 催化净化和换热系统
CN107894171A (zh) * 2017-11-13 2018-04-10 福建奋安铝业有限公司 铝型材生产线余热综合利用系统

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITTO20111023A1 (it) * 2011-11-07 2013-05-08 Stara Glass S P A Forno da vetro provvisto di un gruppo scambiatore di calore
ITTO20130673A1 (it) * 2013-08-05 2015-02-06 Stara Glass S P A Forno da vetro provvisto di un gruppo scambiatore di calore
ES2706877T3 (es) 2014-11-13 2019-04-01 Gerresheimer Glas Gmbh Filtro de partículas de máquina para conformar vidrio, unidad de émbolo, cabeza de soplado, soporte de cabeza de soplado y máquina para conformar vidrio adaptada a dicho filtro o que lo comprende
IT201700073758A1 (it) * 2017-07-05 2019-01-05 Stara Glass S P A Gruppo scambiatore di calore per un forno da vetro
IT202100024635A1 (it) * 2021-09-27 2023-03-27 Univ Degli Studi Genova Gruppi scambiatori di calore per forni da vetro
PL441694A1 (pl) * 2022-07-11 2024-01-15 Forglass Engineering spółka z ograniczoną odpowiedzialnością Układ do poboru gorących gazów z górnej części komór regeneratora pieca szklarskiego i sposób regulacji parametrów gorących gazów pobieranych z górnych części komór regeneratora

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US3764259A (en) * 1972-06-16 1973-10-09 Morgan Construction Co Gas treating apparatus
US4163469A (en) * 1974-09-23 1979-08-07 Hanna Mining Company Heat reclaim system
US4328020A (en) * 1980-11-24 1982-05-04 Ppg Industries, Inc. Melting glass with reduced NOx emissions
US4516934A (en) * 1983-11-25 1985-05-14 Owens-Illinois, Inc. Waste heat recovery from regenerative furnaces
US4528012A (en) * 1984-01-30 1985-07-09 Owens-Illinois, Inc. Cogeneration from glass furnace waste heat recovery
US5754453A (en) * 1995-11-16 1998-05-19 Gas Research Institute Regenerator model for glass furnace reburn analysis
US5893940A (en) * 1997-05-05 1999-04-13 Ppg Industries, Inc. Reduction of NOx emissions in a glass melting furnace
US20050120715A1 (en) * 1997-12-23 2005-06-09 Christion School Of Technology Charitable Foundation Trust Heat energy recapture and recycle and its new applications
US20080289364A1 (en) * 2007-05-23 2008-11-27 Pinkham Jr Daniel Method and system for preheating glass batch or ingredient(s)

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3764259A (en) * 1972-06-16 1973-10-09 Morgan Construction Co Gas treating apparatus
US4163469A (en) * 1974-09-23 1979-08-07 Hanna Mining Company Heat reclaim system
US4328020A (en) * 1980-11-24 1982-05-04 Ppg Industries, Inc. Melting glass with reduced NOx emissions
US4516934A (en) * 1983-11-25 1985-05-14 Owens-Illinois, Inc. Waste heat recovery from regenerative furnaces
US4528012A (en) * 1984-01-30 1985-07-09 Owens-Illinois, Inc. Cogeneration from glass furnace waste heat recovery
US5754453A (en) * 1995-11-16 1998-05-19 Gas Research Institute Regenerator model for glass furnace reburn analysis
US5893940A (en) * 1997-05-05 1999-04-13 Ppg Industries, Inc. Reduction of NOx emissions in a glass melting furnace
US20050120715A1 (en) * 1997-12-23 2005-06-09 Christion School Of Technology Charitable Foundation Trust Heat energy recapture and recycle and its new applications
US20080289364A1 (en) * 2007-05-23 2008-11-27 Pinkham Jr Daniel Method and system for preheating glass batch or ingredient(s)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013034541A1 (de) * 2011-09-06 2013-03-14 Software & Technologie Glas Gmbh (Stg) Verfahren zum betrieb eines regenerativ beheizten industrieofens und regenerativ geheizter industrieofen
CN102853702A (zh) * 2012-09-17 2013-01-02 扬州埃克森能源发展有限公司 一种工业烟气余热极限式回收利用方法
ITTO20120974A1 (it) * 2012-11-08 2014-05-09 Stara Glass S P A Scambiatore di calore di tipo rigenerativo per un forno da vetro
WO2014110879A1 (zh) * 2013-01-18 2014-07-24 北京神雾环境能源科技集团股份有限公司 催化净化和换热系统
CN107894171A (zh) * 2017-11-13 2018-04-10 福建奋安铝业有限公司 铝型材生产线余热综合利用系统

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ES2668966T3 (es) 2018-05-23
TR201807066T4 (tr) 2018-06-21
EP2255143B1 (en) 2018-03-07
PT2255143T (pt) 2018-05-22
ITTO20080052A1 (it) 2009-07-25
WO2009093134A2 (en) 2009-07-30
EP2255143A2 (en) 2010-12-01
WO2009093134A3 (en) 2010-01-07

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Owner name: STARA GLASS S.P.A., ITALY

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