WO2008140410A1 - Brûleur et échangeur de chaleur intégré dans un système combiné de génération de chaleur et d'énergie - Google Patents

Brûleur et échangeur de chaleur intégré dans un système combiné de génération de chaleur et d'énergie Download PDF

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Publication number
WO2008140410A1
WO2008140410A1 PCT/SE2008/050560 SE2008050560W WO2008140410A1 WO 2008140410 A1 WO2008140410 A1 WO 2008140410A1 SE 2008050560 W SE2008050560 W SE 2008050560W WO 2008140410 A1 WO2008140410 A1 WO 2008140410A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
heat exchanger
burner
air
combustion
Prior art date
Application number
PCT/SE2008/050560
Other languages
English (en)
Inventor
Lars Malmrup
Original Assignee
Compower Ab
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 Compower Ab filed Critical Compower Ab
Publication of WO2008140410A1 publication Critical patent/WO2008140410A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/14—Gas-turbine plants characterised by the use of combustion products as the working fluid characterised by the arrangement of the combustion chamber in the plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the present invention relates to a combined heat and power generating system having a burner, which is integrated with a heat exchanger.
  • a heating system comprising a burner and one or more heat exchangers can be used for indirect heating of a fluid.
  • the fluid can be used for heating purposes and/or be the working fluid of a heat engine cycle, e.g. a Brayton cycle, which in combination with a generator can produce electricity.
  • a heat engine cycle e.g. a Brayton cycle
  • the heat exchangers used in the cycle have thus to be designed for sustaining very high temperatures and if the heat transfer primarily is accomplished with convection, it also leads to complicated channel shapes in the heat exchanger. Heat exchangers with complicated channel shapes are very difficult and expensive to manufacture in these high temperature materials.
  • This system furthermore reduces the amount of high temperature material that is needed and makes it possible to manufacture this high temperature heat transferring system part in a simple way. It also makes it possible to use solid fuel in the burner since there are no gas passages for the combustion gas that can get contaminated by matters that can be found in the combustion gases from solid fuels. This is a large problem with the use of normal heat exchangers placed after combustion gases from most solid fuels.
  • the present invention solves these and other problems by providing a combined heat and power generating system comprising a compressor, a turbine and a generator. These components are connected to a main shaft, and the compressor communicates with the turbine through at least one pipe.
  • the system also comprises a recuperator, an integrated burner and heat exchanger, in which the heat from the combustion is transferred by radiation from the flame to the heat exchanger part, which on the heat- exchanger side is connected to a working flow from the recuperator to the turbine.
  • the burner On its other side, the burner is supplied with fuel and air for being combusted in a combustion area of the integrated burner and heat exchanger, wherein the other side of the recuperator is connected to an outlet of the turbine further comprising a recup for preheating air before it enters the heat- exchanger part of the integrated burner and heat exchanger.
  • the heat generation is accomplished by recovering of heat in the combustion gases leaving the integrated burner and heat exchanger.
  • a part of the air leaving the recuperator could be used for heating purposes, either in a heat exchanger or by direct use of the hot air.
  • a part of the air leaving the recuperator or the turbine could be supplied as combustion air to the burner.
  • a part of the air leaving the recuperator is mixed with exhaust gas from the burner before heat recovery is taken place.
  • the heat recovery could takes place in a system that includes condensation of the exhaust gases.
  • the combustion area of the burner could be adapted for combustion of solid fuels, such as wood, grain, coal, or similar.
  • the heat transfer area of the integrated burner and heat exchanger could be arranged as plate and fins.
  • the heat transfer area of the integrated burner and heat exchanger could be arranged as a substrate.
  • the heat transfer area of the integrated burner and heat exchanger could be arranged as a porous body.
  • This system furthermore reduces the amount of high temperature material that is needed and makes it possible to manufacture this high temperature heat transferring system part in a simple way. It also makes it possible to use solid fuel in the burner since there are no gas passages for the combustion gas that can get contaminated by matters that can be found in the combustion gases from solid fuels. This is a large problem with the use of normal heat exchangers placed after combustion gases from most solid fuels.
  • Fig. 1 is a side view of an integrated burner and heat exchanger in partial cross-section
  • Fig. 2 is an end view of the integrated burner and heat exchanger of Fig. 1,
  • Fig. 3 is a schematic view of a combined heat and power generating system according to the present invention
  • Fig. 4 is a schematic view of a second embodiment of the heat and power generating system of the present invention
  • Fig. 5 is a schematic view of a third embodiment of the heat and power generating system of the present invention.
  • a burner 10 with an integrated heat exchanger according to one embodiment of present invention is shown in Fig. 1.
  • the burner and the heat exchanger are integrated in such a way that heat will radiate directly from the combustion flame towards one side of the heat exchanger, in the shown embodiment an inner surface 21 of the heat exchanger.
  • the other side of the inner surface of the heat exchanger is designed in such a way that heat can be transferred to the working flow by convection.
  • the material of the heat exchanger part of the system has high heat conductivity. Thus, the temperature of the heat exchanger will be rather constant and more or less independent of the temperature of the working fluid.
  • the burner system is designed in such a way that it will radiate heat from a relatively large surface. This is accomplished by use of different kinds of flame holders or use of porous material with injection of fuel and air in many locations.
  • the shape of the system can be either substantially cylindrical as in Fig. 1 or have a rectangular or spherical shape. It can also be designed in such a way that it is suitable for burning solid fuel. This means that it shall be possible to dispose of ashes preferable by the force of gravity.
  • the burner with the integrated heat exchanger is only described as a typical example, and other similar solutions are possible where heat from combustion is transferred to an external airflow.
  • One embodiment of a heat exchanger according to the invention is schematically shown in Fig. 1 and in cross- section in Fig. 2.
  • the burner 10 has a nozzle 20, from which fuel and air are introduced for combustion in a combustion area 23, which is surrounded by an inner wall 21 of the heat exchanger.
  • a fluid to be heated is directed to a space 24, which is formed by the inner wall 21 and by an outer housing 22.
  • the space 24 contains fins 25 that are part of the inner wall 21.
  • the fins 25 are designed in such a way that they increase the area for heat transfer as well as combines good heat transfer coefficient with low pressure drop of the air A that shall be heated.
  • Heat is radiated from a flame 15 to the heat exchanger inner wall 21.
  • the heat is also spread by conduction to the fins 25.
  • Typical temperatures of the flame and of the wall 21 and the fins 25 are 1500 C and 1000 C, respectively.
  • a typical temperature of the air A to be heated is 600 C when it enters the heat exchanger and 800 C when it leaves the heat exchanger after it has collected heat from the inner wall 21, the fins 24 and the housing 22.
  • the combustion gas is exhausted through a downstream end of the combustion area 23, where its remaining heat can be recovered.
  • the integrated burner and heat exchanger can be manufactured in different materials, such as heat- resistant steel and/or ceramics. Examples of alternatives to the fins are a substrate similar in shape to exhaust catalysts for cars or a porous material.
  • the integrated burner and heat exchanger is then used as heating means in a Brayton cycle system for combined heat and power generation.
  • a compressor
  • a turbine 2 is interconnected by a main shaft 4, which in turn is connected to a high-speed generator 3.
  • the compressor 1 and the generator 3 are powered by the turbine
  • the air is then directed through a pipe c to the heat exchanger side 24 of the integrated burner and heat exchanger 10, where it is heated by the combustion inside the combustion area 23 of the integrated burner and heat exchanger.
  • the heated air leaving the burner and heat exchanger 10 is brought through a pipe d to the turbine 2, in which the hot air is expanded, which results in mechanical work that drives the compressor and the generator via the main shaft 3.
  • the hot air leaving the turbine 2 is directed through a pipe e to the recuperator 5, for preheating the air that passes on the other side thereof, such as been described above.
  • the recuperator is preferable in this design, since it reduces the heat that must be supplied to the air in the burner and heat exchanger.
  • the air is heated from around 200 C to 600 C in the recuperator and from 600 C to 800 C in the burner and heat exchanger. This makes it possible to use stainless steel in the recuperator; a high temperature material has to be used only for the integrated burner heat exchanger.
  • the burner 10 is supplied with fuel and air through a pipe I.
  • the exhaust gas from the combustion process which still has a rather high temperature, is directed through a pipe j to the a first side of a heat exchanger 7, through pipes m and n, where some heat is transferred to a second side of heat exchanger 7.
  • a gas or a liquid is then directed through the second side of the heat exchanger 7, through pipes m' and n' , where it will collect heat; the collected heat could be used for heating purposes.
  • the heat in the combustion gas leaving the turbine could be recovered in a heat exchanger 6 or being directly fed into a process that has a need for hot air. No heat exchanger is needed in the latter case.
  • the burner circuit and the working air circuits can be provided with valves 11 (fig. 4) and 12 (fig. 5) for allowing use of all or part of the working air leaving the turbine as burner airflow or as mixing flow for obtaining an optimum gas temperature before entering the heat exchanger 7.
  • These valves should be arranged in such a way that no flow in the wrong direction can occur.
  • the pipe e can also be provided with a valve (not shown) for directing a part of the airflow to the burner intake (as combustion air) or to the heat exchanger 7, for mixing with the exhausts from the burner 10.
  • FIG. 4 One embodiment with a three-way valve is shown in Fig. 4, where the three-way valve 11 controls the flow of air leaving the recuperator 5.
  • the air can either be directed through pipe g to a heat exchanger 6, or be supplied as combustion air through the pipe i to the burner 10.
  • the airflow through the turbine 2 is typically much larger than the airflow for the combustion.
  • One reason to use some of the air from after the recuperator as combustion air is that it has a higher temperature and thus can be used for controlling flame temperature for obtaining a good radiation.
  • One example where this will be important is when burning certain solid fuels.
  • Another embodiment is shown in Fig. 5, where the additional three-way valve 12 is provided for controlling the airflow leaving the recuperator 5.
  • the air can be directed to a third three-way valve (not shown) , where the hot exhaust gas from the burner 10 is mixed with the cooler air having exchanged heat in the recuperator 5. This makes it possible to control the temperature of the gases passing through the hot side of the heat exchanger 7.
  • the heat exchanger 7 is arranged such that condensation of the combustion gases takes place. This will give an increased total energy efficiency of the combined heat and power system.
  • the burner flame is typically very hot, more than 1400-1500 °C, and can be controlled by mixing air from after the recuperator, wherein the amount of air from after the turbine is used as combustion air, since the air after the turbine typically has a temperature of 600 0 C.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Supply (AREA)

Abstract

Cette invention concerne un système combiné de génération de chaleur et d'énergie comprenant un compresseur (1), une turbine (2) et un générateur (3) raccordé à un arbre principal (4). Ledit compresseur (1) communique avec la turbine (2) à travers au moins un tuyau (b, c, d). Un récupérateur (5), est relié par un côté à un brûleur et échangeur de chaleur intégré (10) dans lequel la chaleur provenant de la combustion est transférée par rayonnement, de la flamme à la partie formant échangeur de chaleur (21, 22, 24). Ledit brûleur et échangeur de chaleur intégré (10) est relié par son côté formant échangeur de chaleur à un flux de travail allant du récupérateur (5) à la turbine (2) et, par son autre côté, il est alimenté en carburant et en air à brûler dans une zone de combustion (23) de celui-ci. L'autre côté du récupérateur (5) est relié à une sortie de la turbine (2) pour préchauffer l'air avant qu'il ne pénètre dans la partie formant échangeur de chaleur (21, 22, 24) du brûleur et échangeur de chaleur intégré (10). La génération de chaleur est réalisée par récupération de la chaleur des gaz de combustion quittant le brûleur et échangeur de chaleur intégré (10).
PCT/SE2008/050560 2007-05-16 2008-05-14 Brûleur et échangeur de chaleur intégré dans un système combiné de génération de chaleur et d'énergie WO2008140410A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0701181-0 2007-05-16
SE0701181A SE530960C2 (sv) 2007-05-16 2007-05-16 Integrerad brännare och värmeväxlare i ett kombinerat värme- och kraftsystem

Publications (1)

Publication Number Publication Date
WO2008140410A1 true WO2008140410A1 (fr) 2008-11-20

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PCT/SE2008/050560 WO2008140410A1 (fr) 2007-05-16 2008-05-14 Brûleur et échangeur de chaleur intégré dans un système combiné de génération de chaleur et d'énergie

Country Status (2)

Country Link
SE (1) SE530960C2 (fr)
WO (1) WO2008140410A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2405106A1 (fr) * 2010-07-06 2012-01-11 Sib Siber S.p.A. Centrale électrique alimentée à la biomasse
KR101228607B1 (ko) * 2010-12-09 2013-02-01 이엠기술 주식회사 버너의 직,간접열을 이용한 악취공기 연소 탈취장치

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4326382A (en) * 1980-10-24 1982-04-27 E. H. Robbins Power plant
US4492085A (en) * 1982-08-09 1985-01-08 General Electric Company Gas turbine power plant
DE10052844A1 (de) * 2000-10-25 2002-05-16 Pps Pipeline Systems Gmbh Verfahren und Vorrichtung zur Energiegewinnung aus Gas
US6629413B1 (en) * 1999-04-28 2003-10-07 The Commonwealth Of Australia Commonwealth Scientific And Industrial Research Organization Thermodynamic apparatus
GB2417293A (en) * 2004-08-16 2006-02-22 Bowman Power Group Ltd Indirect heating gas turbine system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4326382A (en) * 1980-10-24 1982-04-27 E. H. Robbins Power plant
US4492085A (en) * 1982-08-09 1985-01-08 General Electric Company Gas turbine power plant
US6629413B1 (en) * 1999-04-28 2003-10-07 The Commonwealth Of Australia Commonwealth Scientific And Industrial Research Organization Thermodynamic apparatus
DE10052844A1 (de) * 2000-10-25 2002-05-16 Pps Pipeline Systems Gmbh Verfahren und Vorrichtung zur Energiegewinnung aus Gas
GB2417293A (en) * 2004-08-16 2006-02-22 Bowman Power Group Ltd Indirect heating gas turbine system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2405106A1 (fr) * 2010-07-06 2012-01-11 Sib Siber S.p.A. Centrale électrique alimentée à la biomasse
WO2012004739A2 (fr) 2010-07-06 2012-01-12 Sib Siber S.P.A. Centrale électrique à biomasse
WO2012004739A3 (fr) * 2010-07-06 2012-04-26 Sib Siber S.P.A. Centrale électrique à biomasse
KR101228607B1 (ko) * 2010-12-09 2013-02-01 이엠기술 주식회사 버너의 직,간접열을 이용한 악취공기 연소 탈취장치

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Publication number Publication date
SE0701181L (sv) 2008-11-04
SE530960C2 (sv) 2008-11-04

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