US3187726A - Device for a water boiler provided with an overpressure furnace - Google Patents

Device for a water boiler provided with an overpressure furnace Download PDF

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Publication number
US3187726A
US3187726A US293641A US29364163A US3187726A US 3187726 A US3187726 A US 3187726A US 293641 A US293641 A US 293641A US 29364163 A US29364163 A US 29364163A US 3187726 A US3187726 A US 3187726A
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United States
Prior art keywords
blower
air
gas chamber
combustion gas
blast box
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Expired - Lifetime
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US293641A
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English (en)
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Josephus Franciscus Maria Meul
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/22—Methods of steam generation characterised by form of heating method using combustion under pressure substantially exceeding atmospheric pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B11/00—Steam boilers of combined fire-tube type and water-tube type, i.e. steam boilers of fire-tube type having auxiliary water tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B33/00—Steam-generation plants, e.g. comprising steam boilers of different types in mutual association
    • F22B33/14—Combinations of low and high pressure boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space

Definitions

  • the invention relates to a water boiler provided with an overpressure furnace, with an oil burner, and with a blower for the supply of air.
  • the boiler further includes flue tubes between a flame chest on the rear side of the boiler and a combustion gas chamber on the front side of the boiler.
  • Such a boiler has heretofore been suggested but without success because of substantial difficulties.
  • the box being provided within the combustion gas chamher, the said partitions imposing a zigzag path on the blower air before the same reaches the centrally arranged burner, the blower consisting of a radial compressor with a steep Q-H characteristic, i.e., relatively small change in flow quantity for relatively large pressure variation. Due to these features the combustion air on reaching the burner constitutes a very uniform and pre-heated flow by means of which it is possible to obtain a very stable and effective flame formation in the furnace.
  • a further object of the invention is to achieve a great stability in the operation of the centrifugal blower by connecting the suction side of the blower to a substantially straight duct the length of which is in the order of the distance traversed by the sucked air in about 1 second. Thereby a standing column of air is provided which facilitates starting of the boiler. Also the length of the duct insures a regular flow of air to the blower substantially free of turbulence. 7
  • this duct is of great importance for starting the boiler, since often difiiculties are experienced in the flame formation in the furnace, these ICC difiiculties being avoided due to the application of the said suction duct.
  • the provision of the blast box within the combustion gas chamber not only ensures a heating of the combustion air, but also a cooling of the combustion gases, escaping toward the chimney.
  • the invention further aims at making it possible to use a heavy oil in the burner, without any difiiculties relative .to ignition.
  • FIG. 1 shows a side elevation of the complete boiler installation
  • FIG. 2 is a horizontal longitudinal section to an enlarged scale of the front portion of the boiler according to FIG. 1;
  • FIG. 3 shows on a still further enlarged scale a Variant of a detail of the burner head
  • FIG. 4 is another embodiment of the burner head according to FIG. 3.
  • the water boiler represented in FIG. 1 is built up from a body 1 enclosing a furnace 2, which on the rear side is connected to a flue chest 3, while on the front side there is provided a combustion gas chamber 4.
  • a number of fire or flue tubes 5, connecting the line chest 3 with the combustion gas chamber 4 are arranged in an annular configuration around the furnace 2.
  • the boiler is connected to a chimney by way of an eduction stub 25.
  • the front side of the furnace 2 of the boiler installation which to an enlarged scale is represented in FIG. 2, is provided with an oil burner 6.
  • the boiler operates with air 7 the blast boxfi are two concentrical and tubular interthe front side of the boiler) and mediate partitions 11 and 12, the partition 11 being connected with the front wall 13 of the disc shaped front portion 9 of the blast box, the portion 12 being connected with a conical rear wall 14 of the blast box.
  • a conical shield plate 15 Arranged with spaced relationship in respect to wall 14 is a conical shield plate 15, which is joined'to the end of the tubular intermediate partition 12 protruding into the furnace 2.
  • the blast box 8 is integral with the burner 6 and the blower 7 and is hingedly connected on one side with.
  • FIG. 2 This hinge is visible in FIG. 2 and is constituted by two arms 16 and 17 which are pivotally connected at 18.
  • the sealing between the slewing blast box (constituting the fixed portion of the boiler is formed by two rings 19 and 20 of refractory sealing material, the said rings being positioned against the rear side of the disc shaped frontpart and the outer wall of the cylindrical portion 16, respectively.
  • the stabilizer disc 21, which defines an annular passage between its rim and the tubular wall 12.
  • the annular passage is relatively narrow being only in the order of a few millimeters.
  • a hole is formed in the disc 21 .to allow for the passage of an atomized fuel jet, while in the remaining portion of the disc, helical slits are provided in order to generate a turbulence of the air Within the furnace 2.
  • several connecting strips 22 are provided within the blast box 8.
  • the centrifugal blower 7 is a substantially straight duct 23, the length of which is in the order of the distance which is traversed by the sucked air in about 1 second.
  • the duct 23 has a substantially constant cross-section as. seen in FIG, 1.
  • the free end 24 of the duct opens into the atmosphere.- Due to this column of air in the duct 23 the effect of the blower 7 is improved to such an extent that the difficulties often experienced in starting the boiler installation are entirely eliminated.
  • the centrifugal blower 7 is of the kind having a steep Q-H characteristic (wherein Q represents the while moreover a decrease in sound is obtained.
  • ' stabilizer disc 21 is reduced to a diameter lying within quantity delivered, and H represents the delivery pressure) whereby upon a slight increase of resistance in the. passage of the combustion gases, there is immediately produced an in'crease'of pressure without a noticeable decrease of the output of the blower.
  • the pressure air from the blower 7 enters into the discshaped portion 9 of the blast box 8 and collides with the rear wall of this portion 9 so that the direction of flow is changed.
  • the air flows in a zigzag path through the central cylindrical part 10 around the free protruding ends of the intermediate walls 11 and 12 so as to arrive in the central region of the blast box around the burner 6-and to flow therefrom along and through the stabilizer disc 21 into the furnace 2. It has been found that due to this rather long path covered by the air before arriving in the furnace 2 there is obtained a very uniform flow at the location of the burner 6. Thus, each irregularity due to the direction of flow which the air may have on discharging from the centrifuga-l blower 7 is eliminated.
  • the zigzag track within the blast box 8 can be enlarged by lengthening the tubular intermediate walls 11 and 12 outwardly, the end of the tube 11 which protrudes from the front side of the boiler being closed by a cover, the supply duct for the fuelleading to the oil burner 6 traversing said cover. 7
  • the passage section for theair from the blower 7 in the zigzag path should remain constant or should decrease somewhat, in order to obtain a gradual transformation of pressure into velocity. In this respect it should .be noted that during this transformation the specific vol ume increasesless rapidly than the air velocity.
  • a tubular jacket 25 ' is mounted concentrically around the ,burner 6 within the inner partition wall 12.
  • This jacket has a number of passage holes26 near the front wall 13, said holes serving to feed a quantity of air out of the zig-zag path into the jacket.
  • the size of these holes is such that during operation a pressure inside the jacket is developed, said pressure being smaller than the pressure between the jacket andthe wall 12
  • the decrease of pressure does not exceed 50% of the pressure between the jacket and wall 12.
  • the embodiment according to FIG..4 differs from the variant according to FIG. 3 by the truncated conical end :27 of the jacket 25 joining the central opening 28 in the stabilizer disc 21.
  • a water boiler comprising an overpressure furnace including an oil burner, and a centrifugal blower for the supply of air for said burner, said boiler further including a flue chest and a combustion gas chamber located at opposite ends of the boiler, flue tubes between said flue chest and the combustion gas chamber for the flow of combustion gases from the former to the latter, a substantially straight duct connected to said blower for the supply of air thereto, the duct having a length which is in the order of the distance traversed by the sucked air in about one second, said duct having a substantially constant cross-section and extending proximate the flue chest, combustion gas chamber, and flue tubes, a blast box within the furnace, the pressure side of the blower opening at right angles into said blast box, said blast box including opposite, front and rear walls and at least two interme diate partitions,,said box being adjacent and partially enclosing the combustion gas chamber, said front and rear walls defining a disc-shaped front portion upon which the blower is mounted and a cylindrical portion which is central
  • a water boiler comprising an overpressure furnace having an inlet end and an opposite outlet end, a flue chest and a combustion gas chamber, said flue chest and gas chamber being located at opposite ends of the furnace, flue tubes between said flue chest and said combustion gas chamber for the flow of combustion gases from the furnace via the flue chestand the flue tubes to the bustion gas chamber, a blast box concentric with said burner for the supply of air to said burner, said blast box including a circumferential wall surrounded by the combustion gas chamber, said blast box further including an outwardly directedwall on the front end of said circumferential wall, said outwardly directed wall defining a closure for the front end of the combustion gas chamber, said blast box further including a front wall parallel to and spaced from said outwardly directed wall, a radial air compressor mounted on said front wall and having an opening for discharge of air at right angles to said front wall into the portion of the-blast box between said front wall and said outwardly directed wall, said blast box further having a rear wall extending inwardly from the rear end
  • a Water boiler according to claim 2 comprising a substantially straight inlet duct connected to the blower for the supply of air thereto, said duct having a length which is in the order of the distance traversed by the sucked air in about one second, said duct having a substantially constant cross-section.
  • a water boiler according to claim 2 wherein the air passage sect-ion beginning from the portion of the blast box between the front wall and the outwardly di rected wall to the space around the centrally positioned burner is substantially constant.
  • a Water boiler according to claim 2 comprising a tubular jacket accommodated within the inner intermediate partition and concentrically around the burner, sa-id jacket having a number of passage holes defining a collective inlet area for the supplied air such that during operation, a decrease in pressure inside the jacket occurs which is less than 50% of the pressure outside the jacket.
  • a water boiler according to claim 2 comprising means hingedly securing the blast box to the body of the furnace such that the blast box constitutes one end of the furnace.
  • a water boiler according to claim 2 wherein the partition connected to the front wall is an outer cylindrical partition and the partition connected to the rear wall is an inner cylindrical partition extending within the outer cylindrical partition in spaced relation and surrounding the oil burner, said partitions having ends remote from the walls with which they are respectively connected which are spaced from the other of the walls.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Air Supply (AREA)
US293641A 1962-07-10 1963-07-09 Device for a water boiler provided with an overpressure furnace Expired - Lifetime US3187726A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NL280720 1962-07-10

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US3187726A true US3187726A (en) 1965-06-08

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US (1) US3187726A (tr)
BE (1) BE634420A (tr)
CH (1) CH409299A (tr)
DE (1) DE1451407B2 (tr)
DK (1) DK116241B (tr)
GB (1) GB1053255A (tr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3505980A (en) * 1967-04-24 1970-04-14 Cochran & Co Boilers
US3934556A (en) * 1973-07-11 1976-01-27 Battelle Memorial Institute Boiler using combustible fluid
US4062325A (en) * 1973-07-11 1977-12-13 Pietro Fascione Boiler using combustible fluid

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB254618A (en) * 1926-02-03 1926-07-08 Andrew Laing Improvements relating to liquid fuel furnaces
GB267857A (en) * 1926-12-06 1927-03-24 George Laing Young Improvements in or relating to liquid fuel furnace fronts
US1986914A (en) * 1933-04-13 1935-01-08 Edgar T Avery Heating installation for domestic utilization
US2287057A (en) * 1936-07-27 1942-06-23 Steam And Comb Company Steam production system
US2674981A (en) * 1948-04-28 1954-04-13 Vapor Heating Corp Heat generator
US2835230A (en) * 1954-01-11 1958-05-20 Cleaver Brooks Co Boiler
US2986206A (en) * 1957-02-28 1961-05-30 Shell Oil Co Combustion device for liquid fuel
US3033271A (en) * 1958-12-31 1962-05-08 Vehicules S E V Soc D Et Air-feeding device for oil-burners
US3049173A (en) * 1959-08-31 1962-08-14 Nat Heater Company Inc Burner
US3070151A (en) * 1958-07-09 1962-12-25 Stookunie N V Oilburners

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB254618A (en) * 1926-02-03 1926-07-08 Andrew Laing Improvements relating to liquid fuel furnaces
GB267857A (en) * 1926-12-06 1927-03-24 George Laing Young Improvements in or relating to liquid fuel furnace fronts
US1986914A (en) * 1933-04-13 1935-01-08 Edgar T Avery Heating installation for domestic utilization
US2287057A (en) * 1936-07-27 1942-06-23 Steam And Comb Company Steam production system
US2674981A (en) * 1948-04-28 1954-04-13 Vapor Heating Corp Heat generator
US2835230A (en) * 1954-01-11 1958-05-20 Cleaver Brooks Co Boiler
US2986206A (en) * 1957-02-28 1961-05-30 Shell Oil Co Combustion device for liquid fuel
US3070151A (en) * 1958-07-09 1962-12-25 Stookunie N V Oilburners
US3033271A (en) * 1958-12-31 1962-05-08 Vehicules S E V Soc D Et Air-feeding device for oil-burners
US3049173A (en) * 1959-08-31 1962-08-14 Nat Heater Company Inc Burner

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3505980A (en) * 1967-04-24 1970-04-14 Cochran & Co Boilers
US3934556A (en) * 1973-07-11 1976-01-27 Battelle Memorial Institute Boiler using combustible fluid
US3934555A (en) * 1973-07-11 1976-01-27 Battelle Memorial Institute Boiler using combustible fluid
US4022163A (en) * 1973-07-11 1977-05-10 Pietro Fascione Boiler using combustible fluid
US4062325A (en) * 1973-07-11 1977-12-13 Pietro Fascione Boiler using combustible fluid

Also Published As

Publication number Publication date
DE1451407A1 (de) 1969-01-30
GB1053255A (tr)
CH409299A (de) 1966-03-15
DK116241B (da) 1969-12-22
BE634420A (tr)
DE1451407B2 (de) 1970-10-01

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