US20060225424A1 - Integrated Biomass Energy System - Google Patents

Integrated Biomass Energy System Download PDF

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Publication number
US20060225424A1
US20060225424A1 US11/279,513 US27951306A US2006225424A1 US 20060225424 A1 US20060225424 A1 US 20060225424A1 US 27951306 A US27951306 A US 27951306A US 2006225424 A1 US2006225424 A1 US 2006225424A1
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Prior art keywords
combustion
combustion chamber
air
compressed air
liner
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US11/279,513
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English (en)
Inventor
Gerald Elliott
Carl Linderoth
Clifford McConnell
Alvin Short
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ZILKHA BIOMASS POWER I LLC
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Zilkha Biomass Energy LLC
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Priority to US11/279,513 priority Critical patent/US20060225424A1/en
Assigned to ZILKHA BIOMASS ENERGY LLC reassignment ZILKHA BIOMASS ENERGY LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ELLIOTT, GERALD R., SHORT, ALVIN D., MCCONNELL, CLIFFORD T., LINDEROTH, CARL E.
Publication of US20060225424A1 publication Critical patent/US20060225424A1/en
Assigned to ZILKHA BIOMASS POWER LLC reassignment ZILKHA BIOMASS POWER LLC CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: ZILKHA BIOMASS ENERGY LLC
Priority to US13/008,715 priority patent/US8240123B2/en
Assigned to ZILKHA BIOMASS POWER I LLC reassignment ZILKHA BIOMASS POWER I LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ZILKHA BIOMASS POWER LLC
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/32—Incineration of waste; Incinerator constructions; Details, accessories or control therefor the waste being subjected to a whirling movement, e.g. cyclonic incinerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C3/00—Combustion apparatus characterised by the shape of the combustion chamber
    • F23C3/006—Combustion apparatus characterised by the shape of the combustion chamber the chamber being arranged for cyclonic combustion
    • F23C3/008—Combustion apparatus characterised by the shape of the combustion chamber the chamber being arranged for cyclonic combustion for pulverulent fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/006—General arrangement of incineration plant, e.g. flow sheets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/44—Details; Accessories
    • F23G5/442—Waste feed arrangements
    • F23G5/444—Waste feed arrangements for solid waste
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/44—Details; Accessories
    • F23G5/46—Recuperation of heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G7/00—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals
    • F23G7/10—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of field or garden waste or biomasses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M5/00—Casings; Linings; Walls
    • F23M5/08—Cooling thereof; Tube walls
    • F23M5/085—Cooling thereof; Tube walls using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2202/00—Combustion
    • F23G2202/30—Combustion in a pressurised chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2205/00—Waste feed arrangements
    • F23G2205/18—Waste feed arrangements using airlock systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2205/00—Waste feed arrangements
    • F23G2205/20—Waste feed arrangements using airblast or pneumatic feeding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2206/00—Waste heat recuperation
    • F23G2206/20—Waste heat recuperation using the heat in association with another installation
    • F23G2206/203—Waste heat recuperation using the heat in association with another installation with a power/heat generating installation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2207/00—Control
    • F23G2207/30—Oxidant supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2209/00—Specific waste
    • F23G2209/26—Biowaste
    • 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
    • Y02E20/12—Heat utilisation in combustion or incineration of waste

Definitions

  • biomass waste there are a number of industries that generate large quantities of biomass. Two examples include the forest products and agricultural industries. For example, in the forest product industries, large quantities of biomass are generated, including sawdust, bark, twigs, branches, and other waste wood. Likewise, in the agricultural industries, each crop cycle results in large quantities of biomass, including bagasse, corn cobs, rice hulls, and orchard and vine trimmings. Additional biomass waste that is generated includes sludge and manure. Despite the large quantities that are produced, this waste biomass cannot be easily utilized.
  • biomass has been used heretofore for power generation. Additionally, because biomass is a renewable resource and because biomass releases the same amount of carbon to the atmosphere as it does when it decomposes naturally, the use of biomass for power generation may address several problems with conventionally fossil fuels.
  • gasification One technique that has been developed for using biomass for power generation is gasification.
  • biomass is converted to a combustible gas, which may then be used to generate electricity, for example in a gas turbine.
  • gasification techniques typically have lower thermal efficiencies and higher capital and operating costs than the direct-fired gas turbine power systems discussed below.
  • techniques using solid fuels such as biomass for steam generation also typically have lower thermal efficiencies and higher capital and operating costs than the direct-fired gas turbine power systems discussed below.
  • Gas turbine power systems that operate on solid fuel may be designed as either indirect-fired or direct fired systems. These systems typically have several primary components, including an air compressor, a furnace or combustor, a turbine, and an electric generator.
  • the electric generator and air compressor are driven by energy created by expansion of hot compressed air through the turbine. This hot compressed air for expansion across the turbine is generated by compressing air in the compressor and heating the resultant compressed air with thermal energy generated by the furnace or combustor.
  • the furnace or combustor typically operates as a separate functional unit apart from a functional unit containing the air compressor and the turbine.
  • This design for indirect-firing protects the gas turbine from corrosive effluents and particulate matter typically present in the hot exhaust gases from a furnace or combustor operating on biomass by use of a high temperature heat exchanger.
  • ducts containing the compressed air from the compressor may be placed in close proximity to ducts bearing highly heated exhaust gases from the furnace or combustor, resulting in exchange of heat from the hot exhaust gases to the compressed air.
  • This heated and compressed air then drives the turbine which in turn drives the air compressor and electric generator.
  • these indirect-fired systems have lower thermal efficiencies than direct-fired system.
  • the solid fuel is burned in a pressurized combustor and the heated effluent gases from the combustor are vented directly into the turbine.
  • the combustor is part of an integrated, pressurized unit that includes both the compressor and the turbine.
  • gas cleaning equipment may be employed between the combustor and turbine to reduce the entry of corrosive effluents and particulate matter into the turbine.
  • one aspect of the invention features a cyclonic combustor.
  • the cyclonic combustor comprises a combustion liner forming a combustion chamber having a generally cylindrical shape.
  • the cyclonic combustor further comprises a biomass feed inlet at one end of the combustion chamber formed through the combustion liner for receiving biomass particles under pressure, wherein the biomass feed inlet is formed so that the biomass particles are introduced into the ignition zone of the combustion chamber with a tangential component relative to the longitudinal axis of the combustion liner.
  • the cyclonic combustor comprises a combustion liner forming a combustion chamber having a generally cylindrical shape and having an ignition zone, a combustion zone, and a dilution zone arranged longitudinally along the axis of the combustion chamber.
  • the cyclonic combustor further comprises a biomass feed inlet at one end of the combustion chamber formed through the combustion liner for receiving biomass particles under pressure, wherein the biomass feed inlet is formed so that the biomass particles are introduced into the ignition zone of the combustion chamber with a tangential component relative to the longitudinal axis of the combustion liner.
  • the cyclonic combustor further comprises a plurality of air tuyeres formed through the combustion liner for receiving compressed air, wherein the plurality of air tuyeres are arranged to introduce the compressed air into the combustion chamber with a tangential component relative to the longitudinal axis of the combustion liner, wherein the plurality of air tuyeres are spaced along the length of the combustion liner from about the biomass feed inlet.
  • At least one of the plurality of air tuyeres supplies a sufficient amount of compressed air to the ignition zone for ignition of the biomass particles to begin the combustion.
  • At least one of the plurality of air tuyeres supplies a sufficient amount of compressed air to the combustion zone to complete the combustion of the biomass particles from the ignition zone.
  • at least one of the plurality of air tuyeres supplies a sufficient amount of compressed air to the dilution zone to dilute the combustion gas to a temperature suitable for use in a gas turbine.
  • the system comprises a pressurized feed system that comprises a plurality of chambers wherein a first chamber receives biomass particles at atmospheric pressure and supplies a second chamber with biomass particles under pressure, a first valve positioned at an inlet of the first chamber; a second valve positioned at an outlet of the first chamber to the second chamber; and an air compressor arranged to pressurize the first chamber.
  • the system further comprises a cyclonic combustor for combustion of biomass particles under pressure to produce a combustion gas and particulate ash.
  • the system further comprises a gas turbine that comprises a turbine section comprising an inlet in communication with the combustion chamber for receiving the combustion gas from the combustion chamber, wherein the turbine section is driven by the combustion gas.
  • the gas turbine further may comprise a compressor section driven by the turbine section, wherein the compressor section is arranged to provide the compressed air to the combustion chamber.
  • the system further may comprise an electric generator coupled to the gas turbine for generating electric power, wherein the electric generator is driven by the turbine section.
  • the system comprises a pressurized feed system and a cyclonic combustor for combustion of biomass particles under pressure to produce a combustion gas and ash particulate.
  • the cyclonic combustor comprises a combustion liner forming a combustion chamber having a generally cylindrical shape and having an ignition zone, a combustion zone, and a dilution zone arranged longitudinally along the axis of the combustion chamber.
  • the cyclonic combustor further comprises a biomass feed inlet at one end of the combustion chamber formed through the combustion liner for receiving biomass particles from the pressurized feed system, wherein the biomass feed inlet is formed so that the biomass particles are introduced into the ignition zone of the combustion chamber with a tangential component relative to the longitudinal axis of the combustion liner.
  • the cyclonic combustor further comprises a plurality of air tuyeres formed through the combustion liner for receiving compressed air, wherein the plurality of air tuyeres are arranged to introduce the compressed air into the combustion chamber with a tangential component relative to the longitudinal axis of the combustion liner, wherein the plurality of air tuyeres are spaced along the length of the combustion liner from about the biomass feed inlet. At least one of the plurality of air tuyeres supplies a sufficient amount of compressed air to the ignition zone for ignition of the biomass particles to begin the combustion. At least one of the plurality of air tuyeres supplies a sufficient amount of compressed air to the combustion zone to complete the combustion of the biomass particles from the ignition zone.
  • the system comprises a pressurized feed system and a cyclonic combustor for combustion of biomass particles under pressure to produce a combustion gas and particulate ash.
  • the cyclonic combustor comprises a combustion liner forming a combustion chamber having a generally cylindrical shape.
  • the cyclonic combustor further comprises a biomass feed inlet at one end of the combustion chamber formed through the combustion liner for receiving biomass particles from the pressurized feed system, wherein the biomass feed inlet is formed so that the biomass particles are introduced into the combustion chamber with a tangential component relative to the longitudinal axis of the combustion liner.
  • the cyclonic combustor further comprises a plurality of air tuyeres formed through the combustion liner for receiving compressed air, wherein the plurality of air tuyeres are arranged to introduce the compressed air into the combustion chamber with a tangential component relative to the longitudinal axis of the combustion liner, wherein the plurality of air tuyeres are spaced along the length of the combustion liner from the biomass feed inlet.
  • the system further comprises a cyclonic ash separator.
  • the cyclonic ash separator comprises a choke element comprising an opening of reduced cross-sectional area as compared to the cross-sectional area of the combustion chamber, wherein the choke element has an input in communication with the combustion chamber outlet for receiving the combustion gas from the combustion chamber.
  • Another aspect of the present invention features a method for operating a cyclonic combustor comprising a combustion liner that forms a substantially cylindrically shaped combustion chamber.
  • the method comprises supplying biomass particles to the combustion chamber under pressure, wherein the biomass particles are transferred into the pressurized combustion chamber with a tangential component relative to the longitudinal axis of the combustion chamber.
  • the method further comprises supplying compressed air to the pressurized combustion chamber, wherein the compressed air is supplied to the combustion chamber with a tangential component relative to the longitudinal axis of the combustion chamber so that the biomass particles move through the combustion chamber in a cyclonic motion.
  • the method further comprises burning the biomass particles in the combustion chamber to produce a combustion gas and particulate ash, wherein the combustion gas and the particulate ash move through the combustion chamber in a cyclonic motion.
  • the method further comprises moving a substantial portion of the combustion gas through an opening in a choke element present in the cyclonic combustor, wherein the choke opening has a reduced cross-sectional area as compared to the cross-sectional area of the combustion chamber.
  • the method further comprises allowing at least a portion of the particulate ash to exit the combustion chamber through a particulate ash opening defined between the choke element and the combustion liner.
  • Another aspect of the present invention features another method for operating a cyclonic combustor comprising a combustion liner that forms a substantially cylindrically shaped combustion chamber.
  • the method comprises supplying biomass particles under pressure to an ignition zone of the combustion chamber, wherein the biomass particles are transferred into the ignition zone with a tangential component relative to the longitudinal axis of the combustion chamber.
  • the method further comprises supplying compressed air to the ignition zone of the combustion chamber in an amount sufficient to ignite the combustion of the biomass particles, wherein the compressed air is supplied to the ignition zone with a tangential component relative to the longitudinal axis of the combustion chamber so that the biomass particles rotate in the combustion chamber in a cyclonic motion.
  • the method further comprises moving the ignited biomass particles from the ignition zone of the combustion chamber to a combustion zone of the combustion chamber.
  • the method further comprises supplying compressed air to the combustion zone of the combustion chamber in an amount sufficient to complete the combustion of the biomass particles, wherein the compressed air is supplied to the combustion zone with a tangential component relative to the longitudinal axis of the combustion chamber so that the biomass particles rotate in the combustion chamber in a cyclonic motion.
  • the method further comprises moving the combustion gas and particulate ash produced from combustion of the biomass particles to a dilution zone of the combustion chamber.
  • the method further comprises supplying compressed air to the dilution zone of the combustion chamber in an amount sufficient to dilute the combustion gas to a temperature suitable for use in a gas turbine, wherein the compressed air is supplied to the dilution zone with a tangential component relative to the longitudinal axis of the combustion chamber so that the particulate ash and the combustion gas rotate in the combustion chamber in a cyclonic motion.
  • Another aspect of the invention features a method for direct firing a gas turbine.
  • the method comprises supplying biomass particles to a first chamber at atmospheric pressure and pressurizing the first chamber with compressed air from a compressor.
  • the method further comprises transferring the biomass particles from the pressurized first chamber to a pressurized second chamber.
  • the method further comprises transferring the biomass particles from the pressurized second chamber to a pressurized combustion chamber, the pressurized combustion chamber having a generally cylindrical shape, wherein the biomass particles are transferred into the pressurized combustion chamber with a tangential component relative to the longitudinal axis of the combustion chamber.
  • the method further comprises supplying compressed air to the pressurized combustion chamber, wherein the compressed air is supplied to the pressurized combustion chamber with a tangential component relative to the longitudinal axis of the combustion chamber so that the biomass particles rotate in the combustion chamber in a cyclonic motion.
  • the method further comprises burning the biomass particles in the combustion chamber to produce a combustion gas and particulate ash and separating at least a portion of the particulate ash from the combustion gas.
  • the method further comprises supplying the combustion gas from the combustion chamber to a gas turbine comprising a turbine section and allowing the combustion gas to expand through the turbine section of the gas turbine so as to generate mechanical energy.
  • the method further may comprise driving a compressor section of the gas turbine with the mechanical energy generated by the turbine section so as to produce a compressed air stream.
  • the method further may comprise driving an electric generator with the mechanical energy generated by the turbine section so as to generate electric power.
  • FIG. 1 is a schematic illustration of an example integrated biomass energy system in accordance with one embodiment of the present invention.
  • FIG. 2 is a schematic illustration of an example fuel input system and pressurized feed system in accordance with one embodiment of the present invention.
  • FIG. 3 is a schematic illustration of an example fuel input system and pressurized feed system in accordance with another embodiment of the present invention.
  • FIG. 4 is a schematic illustration of an example combustor in accordance with one embodiment of the present invention.
  • FIG. 5 is a cross-sectional view of the feed inlet taken along lines 5 - 5 of FIG. 4 .
  • FIG. 6 is a cross-sectional view of the air inlet taken along lines 6 - 6 of FIG. 4 .
  • FIG. 7 is a cross-sectional view of the air inlet taken along lines 7 - 7 of FIG. 4 .
  • FIG. 8 is a schematic illustration of an example combustor in accordance with another embodiment of the present invention.
  • FIG. 10 is a schematic illustration of an example combustor containing a cyclonic ash separator in accordance with one embodiment of the present invention.
  • FIG. 1 schematically illustrates a new direct-fired biomass-fueled pressurized gas turbine system.
  • This biomass-fueled pressurized gas turbine system may be particularly suitable for small scale power systems, for example, for the generation of less than about 10 megawatts and, in some examples, in the range of from about 0.5 to about 10 megawatts.
  • the system depicted in FIG. 1 generally comprises pressurized feed system 100 , combustion chamber 110 , cyclonic ash separator 120 , gas turbine 130 , and generator 140 .
  • Biomass particles are supplied to pressurized feed system 100 at substantially atmospheric pressure.
  • An example embodiment of pressurized feed system 100 will be described in more detail with respect to FIGS. 2 and 3 .
  • Pressurized feed system 100 supplies biomass particles to combustion chamber 110 at substantially the operating pressure of combustion chamber 110 through pressurized fuel feed line 102 .
  • Example embodiments of combustion chamber 110 are described in more detail with respect to FIGS. 4 and 8 - 10 .
  • the biomass particles supplied to pressurized feed system may comprise any suitable source of biomass, including, sawdust, bark, twigs, branches, other waste wood, bagasse, corn cobs, rice hulls, orchard and vine trimmings, sludge, manure, and combinations thereof.
  • the biomass particles supplied to the pressurized feed system comprises a wood-based biomass.
  • the biomass particles supplied to the pressurized feed system should have a particle size suitable for cyclonic combustion, for example, the biomass particles may be sized so that they have a major dimension of less than about 3 millimeters (“mm”).
  • biomass particles also should have a moisture content suitable for cyclonic combustion, for example, the biomass particles may be dried so that they have a moisture content of less than about 30% and, preferably, a moisture content in the range of from about 8% to about 16%.
  • cyclonic combustion generally may have different feed requirements (e.g., size, moisture content, etc.) than other types of combustion.
  • the biomass particles are burned in combustion chamber 110 under pressure, for example, at an operating pressure in the range of from about 40 pounds per square inch gauge (“psig”) to about 300 psig, in some examples, in the range of from about 50 psig to about 220 psig, and, in some examples, in the range of from about 100 psig to about 200 psig.
  • Cyclonic combustion of the biomass particles produces ash particulate and a hot, pressurized combustion gas, for example, at a temperature in the range of from about 1,800° F. to about 2,800° F. and, in some embodiments, in the range of from about 2,200° F. to about 2,400° F.
  • combustion chamber 110 operates at about 150 psig and about 2,100° F.
  • Compressed air is also supplied to combustion chamber 110 through compressed air feed line 112 .
  • the compressed air should be supplied into combustion chamber 110 so as to promote cyclonic motion within combustion chamber 110 .
  • the compressed air may be supplied to combustion chamber 110 tangentially.
  • a sufficient amount of the compressed air should also be supplied to combustion chamber 110 to dilute the combustion gas so that it has a temperature suitable for use in gas turbine 130 , for example, a temperature less than about 2,200° F. and, in one example, in the range of from about 1,500° F. to about 2,200° F.
  • Cyclonic ash separator 120 utilizes centrifugal forces to separate ash particulate from the combustion gas. Preferably, at least about 50% of the ash particulate may be separated from the combustion gas.
  • cyclonic ash separator 120 should separate at least a portion (and preferably at least a substantial portion) of the larger ash particulate (e.g., greater than about 10 microns) from the combustion gas but may not separate a substantial portion of the smaller ash particulate (e.g., less than about 1 micron).
  • At least about 80% (preferably, at least about 90%) of ash particulate greater than about 10 microns may be separated from the combustion gas.
  • An example cyclonic ash collector 120 integrated with combustion chamber 110 is described in more detail with respect to FIG. 10 .
  • gas turbine 130 which comprises turbine section 131 and compressor section 132 . Expansion of the combustion gas through turbine section 131 provides mechanical energy to drive compressor section 132 . Expansion of the combustion gas through turbine section 131 also provides the mechanical energy necessary to drive generator 140 for generating electric power.
  • gas turbine 130 may have a single shaft 133 so that both turbine section 131 and compressor section 132 may be driven by a single turbine.
  • turbine section 131 may be comprise two shafts operating at different rotational shaft speeds, for example, a first shaft (not depicted) may be used to drive compressor section 132 and a second shaft (not depicted) may be used to drive generator 140 .
  • Gas turbine 130 may be any suitable gas turbine.
  • gas turbine 130 may be a gas-fired turbine wherein the burner has been replaced by combustion chamber 110 .
  • gas turbine 130 may have any of a variety of pressure ratios, for example, gas turbines suitable for use may have pressure ratios in the range of from about 8:1 to about 20:1.
  • gas turbine 130 may be capable of dual firing, wherein the gas turbine may be fired using an auxiliary fuel, for example, gas, propane, or a liquid fuel.
  • the auxiliary fuel may be used, for example, when pressured feed system 100 and/or fuel input systems 200 , 300 (as depicted in FIGS. 2 and 3 ) are not operating such as when one or both of those systems are down for maintenance
  • Compressor section 132 intakes air via air inlet 134 .
  • Turbine section 131 drives compressor section 132 to compress the air and produce compressed air stream 135 .
  • An auxiliary motor (not depicted) may be used to drive compressor section 132 during startup of the system.
  • a first portion of compressed air stream 135 may be supplied to combustion chamber through compressed air feed line 112 .
  • a second portion 136 of compressed air stream 135 from compressor section 132 may convey the biomass particles from pressurized feed system 100 to combustion chamber 110 in pressurized fuel feed line 102 .
  • a second compressor (not depicted) may be used to further compress this second portion 136 .
  • the second portion 136 of the compressed air stream 135 from compressor section 132 may be cooled by a heat exchanger (not depicted) to avoid combustion of the biomass particles prior to entering the combustion chamber 110 .
  • Exhaust stream 137 obtained by expanding the combustion gas through turbine section 131 may be at or near atmospheric pressure and at a temperature in the range of from about 600° F. to about 1,200° F. and, in some examples, in the range of from about 900° F. to about 1,000° F.
  • exhaust stream 137 may be used directly or indirectly to provide thermal energy for a particular application.
  • exhaust stream 137 may be used to generate steam, heat another fluid that may be used for heating purposes, preheat the biomass particles, and/or dry the biomass particles.
  • exhaust stream 137 may be passed through passed through heat recovery unit 150 (e.g., a heat exchanger) so as to provide thermal energy for a desired application. From heat recovery unit 150 , exhaust stream 152 exits the system through stack 160 .
  • heat recovery unit 150 e.g., a heat exchanger
  • Fuel input system 200 supplies sized and dried biomass particles to pressurized feed system 100 .
  • Fuel input system 200 generally comprises input hopper 210 that can receive biomass particles from one or more sources (e.g., trucks, railcars, conveyor systems, storage bins, silos, etc.).
  • Biomass conveyor 220 moves biomass particles from input hopper 210 to input chamber 230 at substantially atmospheric pressure.
  • Biomass conveyor 220 may be any suitable device for moving the biomass particles to input chamber 230 , for example, biomass conveyor 220 may be a screw conveyor.
  • FIG. 3 schematically depicts an alternate fuel input system 300 .
  • Alternative fuel input system 300 is similar to fuel input system 200 depicted in FIG. 2 except that alternate fuel system further comprises transfer conveyor 310 , sizing equipment 320 , drying equipment 330 , and biomass storage silo 340 .
  • Raw biomass is supplied to alternative fuel input system 300 wherein the raw biomass is sized and dried to produce biomass particles suitable for combustion in combustion chamber 110 .
  • one or more sources may supply raw biomass to input hopper 210 .
  • Transfer conveyor 310 then moves the raw biomass from input hopper 210 to sizing equipment 320 .
  • a front-end loader or other suitable equipment may be used to move the raw biomass to sizing equipment 320 .
  • Sizing equipment 320 may include any equipment suitable for reducing the size of the raw biomass to a suitable size for cyclonic combustion, for example, having a major dimension of less than about 3 mm.
  • sizing equipment 320 may include hogging equipment, grinders, and/or pulverizers.
  • the biomass particles produced by sizing equipment 320 are then transferred to drying equipment 330 .
  • Drying equipment 330 may include any suitable equipment for reducing the moisture content of the biomass particles to a level suitable for cyclonic combustion, for example, a moisture content of less than about 30%.
  • An example of suitable drying equipment 330 may include a rotary-drum type dryer with electric drives.
  • heat recovered from exhaust stream 137 may be used directly or indirectly to provide at least a portion of the heat needed for drying equipment 330 .
  • separation equipment may be used to remove non-fuel materials (e.g., tramp metals) from the raw biomass prior to feed into sizing equipment 320 and drying equipment 330 . Once biomass particles are dried in drying equipment 330 , the sized and dried biomass particles are moved to biomass storage silo 340 .
  • biomass particles may be moved to biomass storage silo 340 using any suitable methodology, for example, they may be pneumatically conveyed.
  • Biomass storage silo 340 may be a closed silo with a capacity sufficient for a particular application.
  • biomass storage silo 340 may have a capacity sufficient to store up to 24-hours of the direct-fired biomass-fueled pressurized gas turbine system's feed requirements so that operation of the system is not interrupted due to temporary unavailability of the raw biomass.
  • Biomass conveyor 220 moves biomass particles from biomass storage silo 340 to input chamber 230 at substantially atmospheric pressure.
  • sizing equipment 320 may include a hogging operation to reduce the raw biomass to a size suitable for use in drying equipment 330 .
  • additional sizing equipment e.g., a grinder, a pulverizer, etc.
  • a grinder e.g., a pulverizer, etc.
  • Pressurized feed system 100 is schematically illustrated by FIGS. 2 and 3 .
  • pressurized feed system 100 receives biomass particles at substantially atmospheric pressure and supplies the biomass particles to combustion chamber 110 under pressure.
  • Pressurized feed system generally comprises input chamber 230 , transfer chamber 240 , feed chamber 250 , and rotary valve 260 .
  • Valves 242 , 244 and air compressor 270 allow the transfer of the biomass particles from input chamber 230 at atmospheric pressure to feed chamber 250 at a pressure greater than the operating pressure of combustion chamber 110 .
  • First valve 242 is positioned at the inlet of transfer chamber 240 and second valve 244 is positioned at the discharge of transfer chamber 240 . While not depicted in FIGS. 2 and 3 , each of valves 242 , 244 may be electrically controlled by a solenoid valve. When open, first valve 242 allows biomass particles in input chamber 230 to move to transfer chamber 240 . When open, second valve 244 allows biomass particles in transfer chamber 240 to move to feed chamber 250 . To maintain pressure in feed chamber 250 , first valve 242 should be closed when second valve 244 is open. Movement of the biomass particles from input chamber 230 to transfer chamber 240 and then to feed chamber 250 generally utilizes gravitational forces. Valves 242 , 244 may be any suitable valve capable of maintaining the pressure differential between transfer chamber 240 and feed chamber 250 while cycling once per minute or even more frequently. For example, valves 242 , 244 may be slide gate valves.
  • Air valve 276 enables pressurization of transfer chamber 240 to a pressure greater than the operating pressure of combustion chamber 110 by introducing compressed air from air reservoir 274 through air line 278 .
  • Air reservoir 274 is supplied compressed air from air compressor 270 via conduit 272 .
  • Valve 246 enables depressurization of transfer chamber 240 , for example, to atmospheric pressure.
  • Feed chamber 250 includes mixer 252 (e.g., a paddle mixer, a ribbon mixer, or other suitable mixing equipment) to prevent (or reduce) the agglomeration of the biomass particles and to facilitate movement of the biomass particles to rotary valve 260 .
  • mixer 252 e.g., a paddle mixer, a ribbon mixer, or other suitable mixing equipment
  • Rotary valve 260 supplies the biomass particles under pressure from feed chamber 250 to pressurized fuel feed line 102 .
  • Rotary valve 260 should be constructed and arranged to feed variable amounts of biomass particles based on the operational requirements of combustion chamber 110 by means of a variable speed drive motor (not depicted).
  • Rotary valve 260 is further constructed and arranged to minimize combustion pulsations in combustion chamber 110 by discharging the smallest amount of biomass particles possible within the constraints imposed by the gravimetric flow characteristics of the biomass particles.
  • the gravimetric flow characteristics of the biomass particles are optimized by the agitation action of the mixer 252 prior to the inlet of the rotary valve 260 .
  • the rotary valve 260 then accepts the biomass particles in especially engineered pockets staggered across the width of the rotary valve.
  • valve pockets controls the amount of biomass particles delivered into the pressurized fuel feed line 102 .
  • the minimal amount of particles in each valve pocket facilitates the smoothest possible delivery of biomass particles to the combustion chamber 110 with minimal pulsations.
  • rotary valve 260 may be mounted inside a pressure vessel so that it can operate under pressure, for example, at a pressure greater than the operating pressure of combustion chamber 110 . In one embodiment, rotary valve 260 operates at about 150 psig.
  • Pressurized feed system 100 may be used to provide a continuous supply of biomass particles to combustion chamber 110 .
  • biomass conveyor 220 supplies biomass particles to input chamber 230 .
  • the flow of biomass particles to transfer chamber 240 is controlled by first valve 242 .
  • First valve 242 may be opened to transfer biomass particles from input chamber 230 to transfer chamber 240 .
  • second valve 244 should be closed when biomass particles are being transferred into transfer chamber 240 .
  • first valve 242 closes and transfer chamber 240 is pressurized.
  • air valve 276 is opened and the compressed air from air reservoir 274 is introduced to transfer chamber 240 .
  • Transfer chamber 240 should be pressurized to a pressure greater than the operating pressure of combustion chamber 110 .
  • Second valve 244 may then open to move the biomass particles under pressure from transfer chamber 240 to feed chamber 250 .
  • Feed chamber 250 is generally maintained under pressure to facilitate the transfer of the biomass particles to combustion chamber 110 .
  • feed chamber 250 may be maintained at a pressure greater than the operating pressure of combustion chamber 110 .
  • first valve 242 should remain closed during transfer of the biomass particles to feed chamber 250 .
  • second valve 244 may be closed, and transfer chamber 240 may be depressurized to atmospheric pressure by opening valve 246 .
  • the pressure cycle in transfer chamber 240 from atmospheric pressure to greater than the operating pressure of combustion chamber 110 may be repeated every minute or even more frequently. However, this pressure cycle may also occur less frequently than once per minute.
  • the transfer of biomass particles to transfer chamber 240 may then be repeated. This cycle time may vary based on a number of factors, including the volume of the biomass particles, the capacity of transfer chamber 230 and feed chamber 240 , and the desired flow rate of biomass particles to combustion chamber 110 .
  • Rotary valve 260 should continuously supply the biomass particles under pressure from feed chamber 250 to pressurized fuel feed line 102 .
  • Second portion 136 of the compressed air stream 135 from compressor section 110 may convey the biomass particles from pressurized feed system 100 to combustion chamber 110 in pressurized fuel feed line 102 .
  • the biomass particles should be supplied to combustion chamber 110 at a rate sufficient to meet the operational requirements of combustion chamber 110 so that the desired power output from gas turbine 130 may be achieved.
  • an air compressor such as air compressor 270 or a second air compressor
  • This air compressor may be used in place of, or in combination with, the pressurized gas from compressor section 110 .
  • FIG. 4 schematically illustrates an example cyclonic combustor 400 for the pressurized combustion of biomass particles in combustion chamber 110 .
  • cyclonic combustor 400 generally comprises a metal outer casing 410 , a combustion liner 420 forming a substantially cylindrically shaped combustion chamber 110 .
  • Cyclonic combustor 400 further comprises a biomass feed inlet 414 formed through combustion liner 420 for receiving biomass particles from pressurized feed system 100 through pressurized fuel feed line 102 .
  • cyclonic combustor further comprises combustion chamber outlet 416 .
  • a plurality of air tuyeres 430 a , 430 b , 430 c , etc. are arranged to introduce compressed air into combustion chamber 110 .
  • Outer casing 410 may have a generally cylindrical shape.
  • Metal outer casing surrounds combustion liner 420 so as to define air feed plenum 412 between outer casing 410 and combustion liner 420 .
  • Combustion liner 420 may have a generally cylindrical shape and defines combustion chamber 110 .
  • Combustion liner 420 should comprise a material that is suitable for the operating conditions of combustion chamber 110 . In some embodiments, the materials may be suitable for temperatures up to about 3,000° F. Examples of suitable materials include refractory materials and metals.
  • Combustion chamber 110 receives biomass particles for combustion through biomass feed inlet 414 at one end of combustion chamber 110 .
  • Biomass feed inlet 414 is formed through outer casing 410 and combustion liner 420 . As illustrated by FIG. 5 , biomass feed inlet 414 should be formed with a tangential component with respect to the longitudinal axis of combustion liner 420 . This arrangement promotes the cyclonic motion of the biomass particles in combustion chamber 110 .
  • Air tuyere 430 a provides compressed air that disperses the biomass particles supplied to combustion chamber 110 .
  • the biomass particles are entrained at a tangential velocity greater than about 80 feet per second (“ft/sec”) and, in some examples, in the range of from about 100 ft/sec to about 200 ft/sec.
  • Combustion chamber 110 generally comprises three different zones, namely, ignition zone 402 , combustion zone 404 , and dilution zone 406 . These three zones are arranged longitudinally along the axis of combustion chamber 110 with ignition zone 402 at one end of combustion chamber 110 and the dilution zone 406 at the other end of combustion chamber 110 . Combustion zone 404 is located between ignition zone 402 and dilution zone 406 .
  • combustion chamber 110 the biomass particles are burned to produce particulate ash and a hot, pressurized combustion gas.
  • the biomass particles enter combustion chamber 110 in ignition zone 402 .
  • ignition zone 402 the biomass particles should be ignited.
  • a sufficient amount of compressed air should be supplied to ignition zone 402 through air tuyeres 430 a , 430 b , 430 c to ignite the biomass particles and facilitate at least partial combustion of the biomass particles.
  • a substoichiometric amount of compressed air may be supplied to ignition zone 402 through air tuyeres 430 a , 430 b , 430 c so that the biomass particles and oxygen in the compressed air react in a substoichiometric combustion.
  • Substoichiometric combustion may be desired, in some examples, to control the flame temperature of the biomass particles so as to reduce the formation of nitrous oxides from the combustion of the biomass particles.
  • Biomass particles and combustion products pass from ignition zone 402 to combustion zone 404 wherein the combustion of the biomass particles is completed.
  • the compressed air supplied to combustion zone 404 by air tuyeres 430 d , 430 e , 430 f , 430 g , 430 h also dilutes the combustion products.
  • the compressed air needed for combustion of the biomass particles and dilution of the combustion products is supplied to combustion chamber 110 through a plurality of air tuyeres 430 a , 430 b , 430 c , etc. formed through combustion liner 420 .
  • the tuyere openings generally may have a conical shape (narrowing towards the combustion chamber), and a length/width aspect ratio exceeding about 2:1 and, in some examples, in a range of 3:1 to 5:1.
  • air tuyeres 430 a , 430 b , 430 c , etc. should be formed with a tangential component with respect to the longitudinal axis of combustion liner 420 .
  • the tuyeres 430 a , 430 b , 430 c , etc. should be constructed and arranged to supply the air needed in each zone of combustion chamber 110 .
  • Rows containing at least one of the plurality of air tuyeres 430 a , 430 b , 430 c , etc. are generally spaced apart along the length of combustion liner 420 with in the range of from about 2 rows to about 20 or more rows. In one example, there are 12 rows spaced along the length of combustion liner 420 . In one example, 4 rows in ignition zone 402 , 5 rows in combustion zone 404 , and 3 rows in dilution zone 406 .
  • Each row may contain from 1 to about 20 or more tuyeres distributed in the same plane.
  • air tuyeres 430 a , 430 b , 430 c , etc. may be arranged in a staggered pattern, wherein the at least one tuyere in each row is displaced 90° along the circumference of combustion liner 420 with respect to the preceding row.
  • air tuyeres 430 b may be displaced 90° along the longitudinal axis of combustion liner 420 with respect to air tuyeres 430 c.
  • each of the plurality of tuyeres 430 a , 430 b , 430 c , etc. may have the same size or different sizes as desired for a particular application.
  • the tuyeres 430 a , 430 b , 430 c , etc. in the same row and/or zone may be the same or different sizes as desired for a particular application.
  • Tuyere size may be adjusted to control the air flow into the zones of combustion chamber 110 and thus control the flame temperature of the biomass particles.
  • the flame temperature may be adjusted to reduce the formation of nitrogen oxides from the combustion.
  • at least one tuyere in each row may increase in size along the length of combustion liner 420 from biomass feed inlet 414 .
  • the tuyeres 430 a , 430 b , 430 c , etc. may linearly increase in size. While not illustrated in FIG. 4 , tuyeres 430 b would be larger than tuyere 430 a , tuyeres 430 c would be larger than tuyeres 430 b with tuyeres 430 i , 430 j , 430 k , 4301 being the largest tuyeres in combustion liner 420 .
  • the tuyeres 430 a , 430 b , 430 c of the ignition zone 402 and the tuyeres 430 d , 430 e , 430 f , 430 g , 430 h of combustion zone 404 may increase in size along the longitudinal axis of combustion chamber 110 from biomass feed line 414 .
  • the tuyeres 430 d , 430 e , 430 f , 430 g , 430 h of combustion zone 404 may be larger than the largest tuyere in ignition zone 402 .
  • the holes in dilution zone 406 may be the same or larger than the largest tuyeres in ignition zone 402 and combustion zone 404 .
  • computational fluid modeling may be used to determine the optimal tuyere size, tangential velocity of the compressed air, the number of tuyeres in each zone of combustion chamber 110 , and the quantity of compressed air supplied to each zone.
  • Combustor 400 further may comprise burner 440 .
  • Burner 440 may operate on an auxiliary fuel, such as natural gas, propane, or a liquid fuel. Burner 440 may be used during start-up of combustor 400 to heat combustion liner 410 to a temperature sufficient to ignite the biomass particulates and/or ignite the biomass particulates for a desired period of time during start up. Burner 440 may be sized for start-up only, or, alternatively, burner 440 may be sized to allow full throughput through the system so that electrical output from generator 140 may remain constant, for example, where the supply of biomass particles may be restricted. In one example, burner 440 is capable of direct firing a gas turbine, such as gas turbine 130 .
  • FIG. 8 schematically illustrates an alternate cyclonic combustor 800 .
  • Cyclonic combustor 800 is similar to cyclonic combustor 400 depicted on FIG. 4 , except that cyclonic combustor 800 comprises a plurality of air feed plenums 810 , 820 , 830 defined between outer casing 410 and combustion liner 420 .
  • the plurality of air feed plenums 810 , 820 , 830 are separated by a plurality of baffles 840 , 850 .
  • Each of the plurality of air feed plenums 810 , 820 , 830 is in communication with at least one of the plurality of air tuyeres 430 .
  • first chamber 810 is in communication with air tuyeres 430 a , 430 b , 430 c .
  • Air tuyeres 430 a , 430 b , 430 c , etc. are supplied air from compressed air feed line 112 via air feed plenums 810 , 820 , 830 .
  • Each of the plurality of air feed plenums 810 , 820 , 830 communicate with a respective portion 112 a , 112 b , 112 c of compressed air feed line 112 from compressor section 132 .
  • compressed air supply into each of the plurality of air feed plenums 810 , 820 , 830 is controlled by a plurality of valves 860 , 870 , 880 , respectively.
  • valve 860 should control the supply of compressed air into ignition zone 402 of combustion chamber 110 to ensure a sufficient supply of compressed air to ignite the biomass particles.
  • Valve 870 should control the supply of compressed air into combustion zone 404 of combustion chamber 110 to ensure a sufficient supply of compressed air to completely combust the biomass particles and begin dilution of the combustion products.
  • Valve 880 should control the supply of compressed air into dilution zone 406 of combustion chamber 110 to ensure a sufficient supply of compressed air to completely dilute the combustion products.
  • FIG. 9 schematically illustrates an alternate cyclonic combustor 900 .
  • Cyclonic combustor 900 is similar to cyclonic combustor 800 depicted on FIG. 8 , except that cyclonic combustor 900 further comprises an intermediate lining 910 having a generally cylindrical shape between outer casing 410 and combustion liner 420 .
  • Cooling plenum 920 is defined between outer casing 410 and combustion liner 420 .
  • Compressed air from compressor section enters cooling plenum 920 through compressed air feed 112 and is pre-heated by radiant heat from combustion chamber 110 thereby cooling combustion chamber 110 . After being pre-heated, this compressed air enters tube 930 which separates into three portions 930 a , 930 b , 930 c .
  • FIG. 10 schematically illustrates an alternate cyclonic combustor 1000 .
  • Cyclonic combustor 1000 is similar to cyclonic combustor 900 depicted on FIG. 9 , except that cyclonic combustor 1000 further comprises cyclonic ash separator 120 and transition assembly 1010 .
  • cyclonic ash separator 120 comprises choke element 1020 , particulate ash opening 1030 formed between choke element 1020 and combustion liner 420 , and ash collection passageway 1040 in communication with combustion chamber 110 via particulate ash opening 1030 .
  • Transition assembly 1010 generally should be constructed and arranged to minimize the transfer of forces from cyclonic combustor 1000 to gas turbine 130 .
  • transition assembly 1010 comprises outer casing 1050 and inner shell 1060 forming a substantially cylindrically shaped combustion gas passageway 1070 .
  • Outer casing 1050 may have a generally conical shape with the wider end adjacent to cooling chamber 110 .
  • outer casing 1050 may have a cylindrical shape or may even be non-circular shaped.
  • Outer casing 1050 surrounds inner shell 1060 so as to define cooling plenum 1080 between outer casing 1050 and inner shell.
  • Transition assembly 1010 should be constructed and arranged so that cooling plenum 1080 of transition assembly 1010 is in communication with cooling plenum 920 of cyclonic combustor 1000 . While not depicted in FIG.
  • outer casing 1050 of transition assembly 1010 may be coupled to outer casing 410 of cyclonic combustor 1000 using any suitable methodology, for example, a bolted flange may be used to couple outer casing 1050 to outer casing 410 .
  • combustion gas passageway 1070 comprising an inlet and an outlet is defined by inner shell 1060 .
  • combustion gas passageway 1070 may be any other suitable shape, for example, non-circular.
  • Combustion gas passageway 1070 may be tapered from cyclonic ash separator 120 to transition assembly outlet 1090 so that the outlet of the combustion gas passageway 1070 has a smaller cross-sectional area than the inlet.
  • Transition assembly 1010 should be constructed and arranged so that combustion gas passageway 1070 is in communication with combustion chamber 110 via opening 1022 in choke element 1020 of cyclonic ash separator 120 .
  • combustion gas In operation, due to the cyclonic motion and high tangential velocity of the combustion gas and particulate ash in combustion chamber 110 , high centrifugal forces are generated thereon. As a result of the centrifugal forces, the particulate ash revolves in combustion chamber 110 adjacent to combustion liner 410 so that the particulate ash passes through particulate ash opening 1030 and passes through ash collection passageway 1040 to ash hopper (not depicted) where it is collected.
  • the combustion gas generally moves from combustion chamber 110 to opening 1022 in choke element 1020 to combustion gas passageway 1070 . While passing through combustion gas passageway 1070 , the combustion gas is cooled by heat exchange with the compressed air in cooling plenum 1080 from compressed air feed 112 .
  • the compressed air passes through cooling plenum 1080 to cooling plenum 920 of combustor 1000 .
  • the combustion gas generally exits transition assembly 1010 via transition assembly outlet 1090 after passing through combustion gas passageway 1070 . This combustion gas is then supplied to gas turbine 130 as depicted in FIG. 1 .
  • Couple or “couples” used herein is intended to mean either an indirect or direct connection. Thus, if a first device couples to a second device, that connection may be through a direct connection, or through an indirect electrical connection via other devices and connections.

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