EP1067335A1 - Heizvorrichtung - Google Patents

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Publication number
EP1067335A1
EP1067335A1 EP99305487A EP99305487A EP1067335A1 EP 1067335 A1 EP1067335 A1 EP 1067335A1 EP 99305487 A EP99305487 A EP 99305487A EP 99305487 A EP99305487 A EP 99305487A EP 1067335 A1 EP1067335 A1 EP 1067335A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
turbine
arrangement
exit gases
heat
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.)
Withdrawn
Application number
EP99305487A
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English (en)
French (fr)
Inventor
Robert Pickering
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP99305487A priority Critical patent/EP1067335A1/de
Publication of EP1067335A1 publication Critical patent/EP1067335A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/34—Burners specially adapted for use with means for pressurising the gaseous fuel or the combustion air
    • F23D14/36—Burners specially adapted for use with means for pressurising the gaseous fuel or the combustion air in which the compressor and burner form a single unit
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L2900/00—Special arrangements for supplying or treating air or oxidant for combustion; Injecting inert gas, water or steam into the combustion chamber
    • F23L2900/05021—Gas turbine driven blowers for supplying combustion air or oxidant, i.e. turbochargers

Definitions

  • the present invention relates to a heating arrangement and, in a preferred embodiment, to a heating arrangement for a domestic boiler.
  • a heat exchanger is arranged over a heat source such as a gas burner in order to heat water (or other heat exchange fluid) passing through the heat exchanger.
  • the heated water is then coupled to heat a hot water supply or a central heating system.
  • known heating arrangements are inefficient and allow up to 65% of the input energy to be unrecovered.
  • GB-A-2273340 (British Gas) discloses a combined heat and power apparatus using a gas turbine to drive the shaft of an electrical power generator, and recovering heat from the exhaust gases of the turbine using a heat exchanger.
  • this known apparatus is relatively large and cumbersome, and is not suited for use in a domestic environment.
  • a supplementary burner is required because the turbine is mainly intended to provide power rather than heat.
  • a heating arrangement for a domestic boiler comprising: a gas turbine arrangement for generating a stream of heated exit gases; a heat exchanger for transferring heat energy from the heated exit gases to a heat exchange fluid; characterised in that the stream of heated exit gases is directed from the turbine arrangement along a longitudinal axis of the turbine arrangement; and a major plane of the heat exchanger lies substantially perpendicular to the axial direction of the heated exit gases.
  • the preferred turbine arrangement operates on the well known principle developed through the use of turbines in aircraft engines and large scale power generation.
  • the aim of the prior art turbine arrangement is to output maximum thrust and minimum heat, whereas the preferred turbine arrangement outputs maximum heat and minimum thrust.
  • the turbine arrangement comprises a turbine fan rotatably mounted within a housing.
  • the clearance between the turbine fan and the housing is usually desired to be as small as possible in order to generate maximum thrust
  • the clearance is relatively large, suitably of the order of 5mm, in order to provide maximum heat output.
  • the clearance is selected so that just sufficient thrust is generated to provide an operational turbine arrangement.
  • a boiler comprising a heat exchanger for transferring heat energy between a gas and a liquid, and a turbine arrangement for generating heated gas directed at the heat exchanger.
  • the turbine arrangement runs on a dry fuel, preferably natural gas.
  • a heat exchanger having a plurality of layers arranged substantially co-planar.
  • each layer comprises an elongate tube bent to form a plurality of parallel sections, and preferably the sections of each adjacent layer are offset with respect to each other.
  • the heat exchanger preferably comprises a plurality of fins for directing air through the heat exchanger.
  • Each fin preferably comprises a planar sheet having parallel ribs formed laterally thereacross and holes therethrough for heat recovery and air scrubbing.
  • Each fin preferably has a deflector arranged at around 45° to the plane thereof, for directing air across the fin.
  • up to around 80 fins are provided across the heat exchanger arranged parallel to the incoming air flow and perpendicular to the heat exchanger layers.
  • a turbine arrangement is shown as will be familiar to persons skilled in the art, having an inlet 102, a front vane carrier 104 and a rear vane carrier 106 carrying front and rear vanes, respectively, for drawing in cold air and compressing and slowing the air.
  • the compressed air is passed to a combustion chamber 120 having gas injectors and atomisers 122 introducing a combustible fluid preferably natural gas from a mains supply.
  • the gas and air mixture is ignited and expands and thus is forced past turbine wheel 130 toward an exit cone 140.
  • the turbine wheel has been developed to produce heat rather than thrust by allowing a relatively large tolerance between the turbine and the surrounding housing 124. If the gap is too great, between the tip of the turbine wheel and the housing, then insufficient energy will be passed to the turbine wheel to sustain the turbine cycle.
  • the shape of the exit cone 140 significantly affects the flame pattern produced from the turbine wheel 130.
  • the exit cone 140 develops the flame pattern and guides it into the heat exchanger.
  • two turbine heat generators 100 are shown arranged side by side and directed toward a heat exchanger 200.
  • a electric motor 300 having a centrifugal clutch is coupled to each of the turbine heat generators 100 to drive the turbine wheels up to operating speed of about 28,000 rpm at start up.
  • Operation of the heating arrangement and boiler system is suitably controlled by a central control means including interlocking sensors and temperature sensors.
  • a central control means including interlocking sensors and temperature sensors.
  • the electric motor When demand for heat is established, such as from a central heating arrangement or a domestic hot water arrangement, the electric motor is engaged to run the or each turbine wheel up to operating speed of about 28,000 rpm. Operating speed is achieved after about 4 seconds, and a valve in the gas supply is opened to supply gas at a first predetermined rate to gas injectors 122 of Figure 1.
  • a sustained flame such as by a suitably placed thermocouple, the gas flow is increased to a second preset level.
  • the speed of the turbine is dependent upon the volume of gas provided, and consequently increases in speed up to a maximum speed of around 80,000 rpm.
  • full working system temperature is achieved within 4 to 5 minutes, and is continually monitored through heating control sensors.
  • the volume of gas supplied is reduced to a rate between the first and second levels and the speed of the turbine consequently drops.
  • the output of the heat generator can be easily varied to match demand.
  • a maximum desired operating output can be achieved within around 10 seconds from start up with the turbine running at around 85,000 rpm and producing an output of around 1010°C.
  • the heat exchanger 200 is suitably coupled to a central heating system or a hot water supply.
  • the boiler can be set to operate on winter or summer settings according to variations in the incoming water temperature.
  • the heat exchanger 200 preferably comprises three layers to provide good thermal transfer efficiency. As may be seen in Figure 3, each layer comprises a tube 202, 203, 204 bent to form a plurality of parallel sections. The middle tube is offset with respect to the top and bottom tubes such that air passing through the heat exchanger must pass around the tube.
  • each fin 220 has a plurality of holes 221 therethrough and lateral ribs 222, for good heat recovery.
  • the fins are preferably set with a minimum amount of clearance. Relatively small gaps are required between the fins due to the relatively high velocity of the heated air exiting the turbine heat generator 100.
  • the arrangement of holes 221, and ribs 222 increase friction to provide an air scrubbing effect which increases efficiency by around 5 to 7%.
  • Each fin is provided with a deflector 223 arranged at around 45° for deflecting air across the fin, and for contributing to the air scrubbing effect.
  • the boiler and heat exchanger does not require a fan or other external venting source, because the residual velocity of the air exiting the heat exchanger is sufficient to ensure adequate venting. Also, relatively long runs of flue ducting may be installed.
  • the heating arrangement described herein has a number of advantages in that it is efficient and compact.
  • a boiler is arranged to fit within the space available in a standard single wall unit of around 300 mm wide by 720 mm high by 280 mm deep.
  • the heating arrangement is efficient with losses only in the region of 43%. Emissions from the heating arrangement are clean and well within current UK and EU standards.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP99305487A 1999-07-09 1999-07-09 Heizvorrichtung Withdrawn EP1067335A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP99305487A EP1067335A1 (de) 1999-07-09 1999-07-09 Heizvorrichtung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP99305487A EP1067335A1 (de) 1999-07-09 1999-07-09 Heizvorrichtung

Publications (1)

Publication Number Publication Date
EP1067335A1 true EP1067335A1 (de) 2001-01-10

Family

ID=8241506

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99305487A Withdrawn EP1067335A1 (de) 1999-07-09 1999-07-09 Heizvorrichtung

Country Status (1)

Country Link
EP (1) EP1067335A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011102955A1 (en) * 2010-02-16 2011-08-25 Circulite, Inc. Test controller for a rotary pump
EP4168712B1 (de) * 2020-06-17 2024-08-07 C.I.B. Unigas S.p.A. Wärmeerzeugungssystem mit einem brenner mit gasturbine zur erzeugung einer flamme

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4002157A (en) * 1974-12-31 1977-01-11 Energy Transformation Corporation Gas turbine heating apparatus
US4098256A (en) * 1976-04-29 1978-07-04 Sieck Charles A Heating system
DE2739655A1 (de) * 1977-09-02 1979-03-08 Max Prof Dr Wutz Waermepumpanlage
US4737102A (en) * 1985-10-25 1988-04-12 Rinnai Corporation Burner for water heater
EP0697572A1 (de) * 1994-08-16 1996-02-21 VIESSMANN WERKE GmbH & CO. Gasheizkessel

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4002157A (en) * 1974-12-31 1977-01-11 Energy Transformation Corporation Gas turbine heating apparatus
US4098256A (en) * 1976-04-29 1978-07-04 Sieck Charles A Heating system
DE2739655A1 (de) * 1977-09-02 1979-03-08 Max Prof Dr Wutz Waermepumpanlage
US4737102A (en) * 1985-10-25 1988-04-12 Rinnai Corporation Burner for water heater
EP0697572A1 (de) * 1994-08-16 1996-02-21 VIESSMANN WERKE GmbH & CO. Gasheizkessel

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011102955A1 (en) * 2010-02-16 2011-08-25 Circulite, Inc. Test controller for a rotary pump
US9841013B2 (en) 2010-02-16 2017-12-12 Circulite, Inc. Test controller for a rotary pump
US20180087500A1 (en) * 2010-02-16 2018-03-29 Circulite, Inc. Test controller for a rotary pump
EP4168712B1 (de) * 2020-06-17 2024-08-07 C.I.B. Unigas S.p.A. Wärmeerzeugungssystem mit einem brenner mit gasturbine zur erzeugung einer flamme

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