US20110005470A1 - Heating apparatus - Google Patents

Heating apparatus Download PDF

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Publication number
US20110005470A1
US20110005470A1 US12/919,836 US91983609A US2011005470A1 US 20110005470 A1 US20110005470 A1 US 20110005470A1 US 91983609 A US91983609 A US 91983609A US 2011005470 A1 US2011005470 A1 US 2011005470A1
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United States
Prior art keywords
flow passage
pipe
gas
combustion
heating apparatus
Prior art date
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Abandoned
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US12/919,836
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English (en)
Inventor
Soichiro Kato
Tsukasa Saitou
Toshiro Fujimori
Katsuyoshi Takahashi
Toshiyuki Suda
Yukinobu Kawaoka
Mamoru Fujii
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IHI Corp
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IHI Corp
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Publication date
Priority claimed from JP2008053901A external-priority patent/JP5211764B2/ja
Priority claimed from JP2008053903A external-priority patent/JP5211765B2/ja
Application filed by IHI Corp filed Critical IHI Corp
Assigned to IHI CORPORATION reassignment IHI CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FUJII, MAMORU, FUJIMORI, TOSHIRO, KATO, SOICHIRO, KAWAOKA, YUKINOBU, SAITOU, TSUKASA, SUDA, TOSHIYUKI, TAKAHASHI, KATSUYOSHI
Publication of US20110005470A1 publication Critical patent/US20110005470A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B7/00—Steam boilers of furnace-tube type, i.e. the combustion of fuel being performed inside one or more furnace tubes built-in in the boiler body
    • F22B7/02—Steam boilers of furnace-tube type, i.e. the combustion of fuel being performed inside one or more furnace tubes built-in in the boiler body without auxiliary water tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/101—Tubes having fins or ribs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/12—Forms of water tubes, e.g. of varying cross-section

Definitions

  • the present invention relates a heating apparatus for heating a fluid to be heated.
  • This application claims the benefit of Japanese Patent Application 2008-053901 filed in Japan on Mar. 4, 2008 and Japanese Patent Application 2008-053903 filed in Japan on Mar. 4, 2008, the entire disclosure of which is incorporated by reference herein.
  • a small heating apparatus may be installed for the heating of water for use in bathing or for steaming during cooking.
  • a heating apparatus has been disclosed which heats water flowing in a pipe using high-temperature combustion gas produced by combustion of a fuel in the presence of combustion air to thereby evaporate the water into steam.
  • the heating apparatus may be also used for heating of various liquids (a liquid to be heated) (Patent Literature 1).
  • Patent Literature 1 Japanese Patent Application, First Publication No. 2007-139358
  • a large combustion chamber must be provided in order to maintain the time for complete combustion within the combustion chamber.
  • combustion gas has a considerably high temperature, there is the possibility that the uncombusted gas may undergo spontaneous combustion as a result of excessive heating prior to supply of the uncombusted gas to the combustion chamber and that flame propagation may occur thereby resulting in occurrence of combustion outside of the combustion chamber.
  • a large amount of heat is radiated to the periphery from a large combustion chamber, and thereby results in a reduction in energy efficiency.
  • the present invention is proposed in light of the above problems, and has the object of providing a heating apparatus for heating of a liquid to be heated that reduces the size of a combustion chamber, stabilizes the flame in the combustion chamber and thereby improves energy efficiency.
  • the present invention is a heating apparatus for heating of a liquid to be heated including a first flow passage in which uncombusted gas that contains a combustible fuel is injected from a nozzle hole that is smaller than the flame quenching distance at a flow speed to thereby enable flame maintenance and is combusted, and thereby enables flow of combustion gas resulting from the combustion, and a second flow passage enabling flow of uncombusted gas supplied through the nozzle hole.
  • the above configuration may form the second flow passage about the first flow passage.
  • uncombusted gas is heated by flowing through the second flow passage formed about the first flow passage which enables flow of the combustion gas.
  • the entire periphery of the second flow passage does not make contact with the first flow passage. Therefore a part of the heat amount transmitted from the combustion gas is radiated from the uncombusted gas.
  • a third flow passage is surrounded by the first flow passage and enables flow of a liquid to be heated.
  • a configuration in which the third flow passage is formed from an inner space of a third pipe, a configuration in which the first flow passage is formed from a space sandwiched by the third pipe and the first pipe concentrically enclosing the third pipe, and a configuration in which the second flow passage is formed from a space sandwiched by the first pipe and the second pipe concentrically enclosing the first pipe are enabled.
  • a plurality of fins may be provided to project towards the first flow passage from an outer peripheral face of the third pipe.
  • the third pipe is curved toward the first flow passage side and the second flow passage side at a predetermined interval.
  • a configuration is possible in which the first flow passage is formed about the second flow passage, and the third flow passage enables flow of the liquid to be heated and is formed about the first flow passage.
  • the first flow passage is formed about the second flow passage that enables flow of uncombusted gas, and combustion gas flows in the first flow passage.
  • the uncombusted gas flowing in the second flow passage is heated by high-temperature combustion gas which flows in the first flow passage.
  • a stable flame is formed by injection of uncombusted gas from the second flow passage at a flow speed enabling maintenance of a flame through a nozzle hole that is set to be smaller than the flame quenching distance.
  • the third flow passage is formed about the first flow passage which enables combustion of uncombusted gas by the stable flame and flow of the uncombusted gas, and the liquid to be heated flows in the third flow passage.
  • a guide portion may be provided to guide the combustion gas from the first flow passage to a region opposite the first flow passage that is a region on an outer side of the third flow passage.
  • the second flow passage is configured from an inner space in the second pipe
  • the first flow passage is configured from the space sandwiched by the second pipe and the first pipe that concentrically surrounds the second pipe
  • the third flow passage is configured from the space sandwiched by the first pipe and the third pipe that concentrically surrounds the first pipe.
  • the second flow passage is configured from an inner space in the second pipe
  • the third flow passage is configured from the inner space of a plurality of fourth pipes disposed at a distance from the second pipe centering on the second pipe
  • the first flow passage is configured from a space surrounded by the second pipe and the partitions closing the interval between the pairs of fourth pipes and fourth pipes.
  • the second passage which enables flow of the uncombusted gas is formed about the first flow passage which enables flow of the combustion gas. Therefore although the entire periphery of the second flow passage does not come into contact with the first flow passage, a part of the heat amount transmitted from the combustion gas is radiated from the uncombusted gas. As a result, in addition to reduce the size of a combustion chamber by heating uncombusted gas, overheating of the uncombusted gas can be suppressed, and it is possible to form a stable flame in the combustion chamber. Therefore the combustion chamber in the heating apparatus that heats the liquid to be heated can be reduced in size and maintenance of a stable flame in the combustion chamber is possible.
  • the first passage is formed about the second flow passage which enables flow of the uncombusted gas and the combustion gas flows in the first passage. Therefore the uncombusted gas flowing in the second passage can be heated by the high-temperature combustion gas flowing in the first flow passage. Furthermore a stable flame is formed by injection of uncombusted gas from the second flow passage at a flow speed enabling maintenance of a flame through a nozzle hole that is set to be smaller than the flame quenching distance. This stable flame enables stable combustion even when coming into direct contact with the partition face making contact with the cold liquid to be heated, and enables efficient transmission of heat to the partition face.
  • the third flow passage is formed about the first flow passage in which the uncombusted gas is combusted by the stable flame and enables flow of the combustion gas, and the liquid to be heated flows in the third flow passage.
  • the liquid to be heated flowing in the third flow passage is heated by direct heating of the third flow passage by the stable flame. Therefore in comparison to use of a passage for the liquid to be heated that is heated only by combustion gas, since the heat amount is effectively transmitted to the liquid to be heated, it is possible to improve the energy efficiency of the heating apparatus that heats the liquid to be heated.
  • Uncombusted gas flowing in the second flow passage is heated by high-temperature combustion gas flowing in the first flow passage, the heated uncombusted gas is injected from the second flow passage at a flow speed enabling maintenance of a flame through a nozzle hole that is set to be smaller than the flame quenching distance, and the uncombusted gas is combusted. Since this configuration enables sufficient heating of the uncombusted gas by the high-temperature combustion gas, there is no need for a large combustion chamber to enable stable combustion, and therefore enables continuous combustion in the microchannels of the combustion chamber. Therefore the combustion chamber can be downsized thereby enabling reduction in size of the heating apparatus.
  • FIG. 1 is a perspective view showing a schematic configuration of a small boiler according to a first embodiment of a heating apparatus of the present invention.
  • FIG. 2 is a horizontal sectional view of the schematic configuration of the apparatus shown in FIG. 1 .
  • FIG. 3 is a vertical sectional view of the schematic configuration of the apparatus shown in FIG. 1 .
  • FIG. 4 is a vertical sectional view of the schematic configuration of the small boiler according to a second embodiment of the present invention.
  • FIG. 5 is a horizontal sectional view of the schematic configuration of the small boiler according to a third embodiment of the present invention.
  • FIG. 6 is a horizontal sectional view of the schematic configuration of the small boiler according to a fourth embodiment of the present invention.
  • FIG. 7 is a perspective view of the schematic configuration of the small boiler according to a fifth embodiment of the present invention.
  • FIG. 8 is a horizontal sectional view of the schematic configuration of the apparatus shown in FIG. 7 .
  • FIG. 9 is a vertical sectional view of the schematic configuration of the apparatus shown in FIG. 7 .
  • FIG. 10 is a horizontal sectional view of the schematic configuration of the small boiler according to a sixth embodiment of the present invention.
  • FIG. 11 is a perspective view of the schematic configuration of the apparatus shown in FIG. 10 .
  • FIG. 12 is a horizontal sectional view of the schematic configuration of the small boiler according to a seventh embodiment of the present invention.
  • FIG. 13 is a horizontal sectional view of the schematic configuration of the small boiler according to an eighth embodiment of the present invention.
  • a first embodiment of a heating apparatus according to the present invention will be described below making reference to the figures and using an example of a small boiler.
  • the dimensions of respective members have been suitably varied to a size that enables recognition of each member.
  • FIG. 1 to FIG. 3 are schematic views of a small boiler B 1 according to the present embodiment.
  • FIG. 1 is a perspective view
  • FIG. 2 is a horizontal sectional view
  • FIG. 3 is a vertical sectional view.
  • a small boiler B 1 according to the present embodiment has a three-layered structure in which a first pipe 1 (first pipe), a second pipe 2 (second pipe), a third pipe 3 (third pipe) are disposed concentrically when viewed horizontally.
  • the first pipe 1 extends in a vertical direction and the lower end 11 thereof is closed.
  • a plurality of nozzle holes 12 set so that the diameter thereof is smaller than the flame quenching distance of the uncombusted gas is provided in a side partition portion near to the lower end 11 .
  • the first pipe 1 is formed from a material that has superior heat transmission characteristics (for example, brass or the like).
  • the second pipe 2 extends vertically and concentrically surrounds the first pipe 1 .
  • a lower end 21 thereof is closed, and in the same manner as the first pipe 1 , it is formed from a material having superior heat transmission characteristics.
  • the third pipe 3 extends vertically and is inserted into the first pipe 1 .
  • a lower end 31 thereof is closed, and in the same manner as the first pipe 1 and the second pipe 2 , the third pipe 3 is preferably formed from a material having superior heat transmission characteristics.
  • An inner space in the third pipe 3 forms a water flow passage R 3 (third flow passage) which enables flow of the water (liquid to be heated) W.
  • the water flow passage R 3 is configured from the inner space of the third pipe 3 .
  • a water supply portion (not shown) to supply water W to the water flow passage R 3 is connected in proximity to the lower end of the water flow passage R 3 .
  • a regulated flow amount of water W is supplied to the water flow passage R 3 by the water supply portion.
  • a discharge portion (not shown) is connected to enable discharge of steam produced by evaporation of water W in the water flow passage R 3 in proximity to the upper end of the water flow passage R 3 .
  • a regulated amount of steam is discharged to an external portion from the water flow passage R 3 via the discharge portion.
  • a space sandwiched by the third pipe 3 and the first pipe 1 forms a combustion gas flow passage R 1 (first flow passage) in which s combustion of uncombusted gas G 1 occurs and combustion gas G 2 produced by combustion of the uncombusted gas G 1 can flow.
  • the combustion gas flow passage R 1 is configured from a space sandwiched by the third pipe 3 and the first pipe 1 that concentrically surrounds the third pipe. Furthermore the water flow passage R 3 is surrounded by the combustion gas flow passage R 1 .
  • a section near to the lower end of the combustion gas flow passage R 1 (near to the nozzle hole 12 ) forms a combustion chamber K in which uncombusted gas G 1 injected from the nozzle holes 12 is combusted.
  • An ignition apparatus (not shown) is provided in the combustion chamber K.
  • a space sandwiched by the first pipe 1 and the second pipe 2 forms the uncombusted gas flow passage R 2 (second flow passage) that enables flow of uncombusted gas G 1 including combustible fuel.
  • the uncombusted gas flow passage R 2 is configured from a space sandwiched by the first pipe 1 and the second pipe 2 that concentrically covers the first pipe 1 .
  • the upper end portion of the second pipe 2 is connected to an uncombusted gas supply apparatus (not shown) that supplies uncombusted gas G 1 to the uncombusted gas flow passage R 2 .
  • the uncombusted gas G 1 may be a mixed gas of fuel with an oxidation agent.
  • the fuel may be an oil fuel, natural gas or the like.
  • firstly uncombusted gas G 1 is supplied from the uncombusted gas supply apparatus that is connected to the second pipe 2 to the uncombusted gas flow passage R 2 .
  • the uncombusted gas G 1 injected from nozzle holes 12 formed in the first pipe 1 is ignited and combusted to thereby form a flame in the combustion chamber K.
  • the combustion gas G 2 produced by the combustion of the uncombusted gas G 1 flows through the combustion gas flow passage R 1 and is discharged.
  • the uncombusted gas G 1 heated by heat exchange with the combustion gas G 2 is injected in a heated state into an inner portion of the first pipe 1 through the nozzle holes 12 .
  • the uncombusted gas G 1 is injected from the nozzle holes 12 and combusted in the combustion chamber K.
  • the nozzle holes 12 formed in the first pipe 1 are set to be smaller than the flame quenching distance of the uncombusted gas G 1 in the combustion environment of the combustion chamber K, it is possible to suppress propagation of the flame to the uncombusted gas flow passage R 2 . Furthermore since the uncombusted gas flow passage R 2 is formed about the combustion gas flow passage R 1 , the entire periphery of the uncombusted gas flow passage R 2 does not come into contact with the combustion gas flow passage R 1 , and a part of the heat amount transmitted from the combustion gas G 2 is radiated from the uncombusted gas G 1 .
  • uncombusted gas G 1 supplied to the combustion chamber K through the uncombusted gas flow passage R 2 is heated by the combustion gas G 2 flowing through the combustion gas flow passage R 1 in a state in which combustion in the combustion chamber K is continuously executed. Therefore, a stable flame can be formed by a combustion chamber K which is extremely small in comparison to the combustion chamber in a conventional heating apparatus.
  • Water W in the water flow passage R 3 is heated and evaporated by the combustion gas G 2 in the combustion gas flow passage R 2 and the flame in the combustion chamber K in a state in which a stable flame is formed in the combustion chamber K and combustion is continuously executed. More specifically, heat produced by combustion is transmitted to water W through the second pipe 2 that functions as a heat exchange partition, and therefore the water W is heated and evaporates. The steam produced by evaporation of the water W is discharged to an external portion of the small boiler B 1 through the discharge portion (not shown). Since the water flow passage R 3 is surrounded by the combustion gas flow passage R 1 , a heat amount can be transmitted to the water W from the entire periphery of the water flow passage R 3 and thereby enables efficient heating of the water W.
  • an uncombusted gas flow passage R 2 which enables flow of the uncombusted gas G 1 is formed about the combustion gas flow passage R 1 which enables flow of the combustion gas G 2 . Consequently, the entire periphery of the uncombusted gas flow passage R 2 makes no contact with the combustion gas flow passage R 1 , and a portion of the heat amount transmitted from the combustion gas G 2 is radiated from the uncombusted gas G 1 .
  • the combustion chamber K can be made smaller due to the heating of the uncombusted gas G 1 , and it is possible to suppress the overheating of the uncombusted gas G 1 and stabilize the flame in the combustion chamber K. Therefore the combustion chamber K can be made smaller and the flame in the combustion chamber K can be stabilized.
  • FIG. 4 is a vertical sectional view of the schematic configuration of a small boiler B 2 according to an embodiment.
  • the small boiler B 2 according to the present embodiment includes a fourth pipe 4 which concentrically surrounds the second pipe 2 .
  • a space sandwiched by the second pipe 2 and the fourth pipe 4 is formed as a storage portion 5 that stores water W and is connected to the water flow passage R 3 .
  • the small boiler B 2 in the present embodiment having the above configuration, although water W stored temporarily in the water storage portion 5 is supplied to the water flow passage R 3 , the water W receives a portion of the heat amount radiated from the uncombusted gas G 1 in the storage portion 5 . Consequently, the amount of heat radiated from the uncombusted gas G 1 can be used to heat the water W, and therefore enables more efficient heating of the water W.
  • FIG. 5 is a horizontal sectional view of the schematic configuration of a small boiler B 3 according to an embodiment.
  • the small boiler B 3 according to the present embodiment includes a plurality of fins 10 that project towards the combustion gas flow passage R 1 from an outer peripheral face of the third pipe 3 .
  • the fins 10 are integrally formed with the third pipe 3 and are formed from a material having superior heat transmission characteristics in the same manner as the third pipe 3 .
  • the fins 10 enable an increase in the heat exchanging surface area with water W flowing through the water flow passage R 3 and the combustion gas G 2 flowing through the combustion gas flow passage R 1 , and thereby enable more efficient heating of the water.
  • FIG. 7 is a horizontal sectional view of the schematic configuration of a small boiler B 4 according to an embodiment.
  • the small boiler B 4 according to the present embodiment is such that the second pipe 2 is configured in a star shape that is curved toward the combustion gas flow passage R 1 and the water flow passage R 3 at a fixed interval.
  • the formation of the third pipe 3 into a star shape which is curved at a fixed interval enables an increase in the heat exchanging surface area with water W flowing through the water flow passage R 3 and the combustion gas G 2 flowing through the combustion gas flow passage R 1 , and thereby enables more efficient heating of the water.
  • FIG. 7 to FIG. 9 are schematic views of a small boiler B 101 according to a fifth embodiment of the present invention.
  • FIG. 7 is a perspective view
  • FIG. 8 is a horizontal sectional view
  • FIG. 9 is a vertical sectional view.
  • a small boiler B 101 according to the present embodiment has a three-layered structure in which a first pipe 101 (first pipe), a second pipe 102 (second pipe), a third pipe 103 (third pipe) are disposed concentrically when viewed horizontally.
  • the second pipe 102 extends vertically and a lower end 111 thereof is closed. A plurality of nozzle holes 112 set so that the diameter thereof is smaller than the flame quenching distance of the uncombusted gas is provided in a side partition portion near to the lower end 111 .
  • the second pipe 102 is formed from a material that has superior heat transmission characteristics (for example, brass or the like).
  • the inner space in the second pipe 102 forms an uncombusted gas flow passage R 2 (second flow passage) which enables flow of the uncombusted gas G 1 including combustible fuel. More specifically, in the small boiler B 101 according to the present embodiment, the uncombusted gas flow passage R 2 is configured from the inner space of the second pipe 102 .
  • An upper end portion of the second pipe 102 is connected to the uncombusted gas supply passage (not shown) that supplies uncombusted gas G 1 to the uncombusted gas flow passage R 2 .
  • the uncombusted gas G 1 may be a mixture gas of fuel with an oxidation agent.
  • the fuel may be an oil fuel, natural gas or the like.
  • the first pipe 101 extends vertically and is disposed to concentrically surround the second pipe 102 .
  • a lower end 121 thereof is closed, and in the same manner as the second pipe 102 , it is formed from a material displaying superior heat transmission characteristics.
  • a space sandwiched by the first pipe 101 and the second pipe 102 forms a combustion gas flow passage R 1 (first flow passage) which enables combustion of uncombusted gas G 1 and enables flow of the combustion gas G 2 produced by the combustion of uncombusted gas G 1 .
  • the combustion gas flow passage R 1 is configured from a space sandwiched by the second pipe 2 and the first pipe 101 that concentrically surrounds the second pipe 2 .
  • An ignition apparatus (not shown) is provided in the combustion chamber K.
  • the third pipe 103 extends vertically and is disposed to concentrically surround the first pipe 101 .
  • a lower end 131 thereof is closed, and it is preferred that the third pipe 3 is formed from a material displaying low heat transmission characteristics.
  • a space sandwiched by the first pipe 101 and the third pipe 103 forms a water flow passage R 3 (third flow passage) which enables flow of the water (liquid to be heated) W. More specifically, in the small boiler B 101 according to the present embodiment, the water flow passage R 3 is configured from a space sandwiched by the first pipe 101 and the third pipe 103 that concentrically surrounds the first pipe 101 .
  • a water supply portion for supplying water to the water flow passage R 3 is connected to a section near to the lower end of the water flow passage R 3 , and a regulated flow amount of water W is supplied to the water flow passage R 3 by the water supply portion.
  • a discharge portion for discharging steam produced by evaporation of water W in the water flow passage R 3 is connected in proximity to an upper end of the water flow passage R 3 , and a regulated flow amount of steam is discharged from the water flow passage R 3 to an external portion by the discharge portion.
  • a small boiler B 101 In a small boiler B 101 according to the present embodiment having the above configuration, firstly uncombusted gas G 1 is supplied from the uncombusted gas supply apparatus that is connected to the second pipe 102 to the uncombusted gas flow passage R 2 .
  • the uncombusted gas G 1 injected from nozzle holes 112 formed in the second pipe 102 is ignited and combusted to thereby form a flame in the combustion chamber K.
  • the combustion gas G 2 produced by the combustion of the uncombusted gas G 1 flows through the combustion gas flow passage R 1 and is discharged.
  • the uncombusted gas G 1 heated by heat exchange with the combustion gas G 2 is ejected into an outer portion of the second pipe 102 through the nozzle holes 112 in a state of being heated to almost an ignition temperature.
  • the uncombusted gas G 1 ejected from the nozzle holes 112 is ignited by the flame formed in the combustion chamber K, and is combusted.
  • the nozzle holes 112 formed in the second pipe 102 are set to be smaller than the flame quenching distance of the uncombusted gas G 1 in the combustion environment of the combustion chamber K, the flame does not propagate to the uncombusted gas flow passage R 2 . Consequently the flame is stabilized in the combustion chamber K, and thereby enables continuous combustion.
  • uncombusted gas G 1 supplied to the combustion chamber K through the uncombusted gas flow passage R 2 is heated by the combustion gas G 2 flowing through the combustion gas flow passage R 1 in a state in which combustion in the combustion chamber K is continuously executed. Therefore, a stable flame can be formed by a combustion chamber K which is extremely small in comparison to the combustion chamber in a conventional heating apparatus.
  • Water W in the water flow passage R 3 is heated and evaporated by the combustion gas G 2 in the combustion gas flow passage R 1 and the flame in the combustion chamber K in a state in which a stable flame is formed in the combustion chamber K and combustion is continuously executed. More specifically, a heat amount of the flame and a heat amount of the combustion gas G 2 are transmitted to the water W through the first pipe 101 that functions as a heat exchange partition, and therefore the water W is heated and evaporated.
  • the steam produced by evaporation of the water W is discharged to an external portion of the small boiler B 101 through the discharge portion (not shown).
  • a combustion gas flow passage R 1 in which combustion gas G 2 flows is formed about the uncombusted gas flow passage R 2 which enables flow of the uncombusted gas G 1 . Consequently, the uncombusted gas G 1 flowing in the uncombusted gas flow passage R 2 is heated by the combustion gas G 2 that flows in the combustion gas flow passage R 1 . Furthermore a stable flame is formed by injection of uncombusted gas G 1 from the uncombusted gas flow passage R 2 at a flow speed enabling maintenance of a flame through a nozzle holes 112 that are set to be smaller than the flame quenching distance. This stable flame is enabled even when coming into direct contact with the partition face (first pipe 101 ) making contact with the cold liquid.
  • the water flow passage R 3 is formed about the combustion gas flow passage R 1 which forms the stable flame and water W is supplied to the water flow passage R 3 .
  • the water W that flows in the third flow passage is heated by direct heating of the water flow passage R 3 by the stable flame. Therefore in comparison to heating the water flow passage R 3 only by combustion gas G 2 , the amount of heat can be efficiently transmitted to the water W. Consequently, the small boiler B 101 of the present embodiment enables an improvement in energy efficiency.
  • the uncombusted gas G 1 flowing in the combusted gas flow passage R 2 is heated by high-temperature combustion gas G 2 flowing in the combustion gas flow passage R 1 , the heated uncombusted gas G 1 is combusted by ejection from the uncombusted gas flow passage R 2 at a flow speed enabling maintenance of a flame through a nozzle hole 112 that is set to be smaller than the flame quenching distance.
  • the adoption of the above configuration enables sufficient heating of the uncombusted gas G 1 by the high-temperature combustion gas G 2 , and therefore enables continuous stable combustion in a small combustion chamber K.
  • the combustion chamber can be made smaller thereby enabling downsizing of the apparatus.
  • FIG. 10 and FIG. 11 are schematic views of a small boiler B 102 according to a fifth embodiment of the present invention.
  • FIG. 10 is a horizontal sectional view and
  • FIG. 11 is a perspective view.
  • the uncombusted gas flow passage R 2 of the small boiler B 102 according to the present embodiment is configured from an inner space in the second pipe 102 in the same manner as the small boiler B 101 in the fifth embodiment.
  • the water flow passage R 3 is configured from the inner space of a plurality of fourth pipes 104 disposed at a distance from the second pipe 102 centering on the second pipe 102 , and the combustion gas flow passage R 1 is configured from a space surrounded by partitions 105 closing the second pipe 102 and the space between the pairs of fourth pipes 104 and fourth pipes 104 .
  • the height of the partition 105 is set to be low in comparison with the height of the second pipe 102 and the fourth pipe 104 .
  • the space functions as a guide portion 106 for guiding the combustion gas G 2 into a region on an outer side of the water flow passage R 3 and opposite the combustion gas flow passage R 1 .
  • FIG. 12 is a horizontal sectional view of the schematic configuration of a small boiler according to a seventh embodiment of the present invention.
  • the small boiler B 103 according to the present embodiment includes a plurality of fins 110 that project towards the water flow passage R 3 from an outer peripheral face of the first pipe 101 .
  • the fins 110 are integrally formed with the first pipe 101 and are formed from a material having superior heat transmission characteristics in the same manner as the first pipe 101 .
  • the fins 110 enable an increase in the heat exchanging surface area with water W flowing through the water flow passage R 3 and the combustion gas G 2 flowing through the combustion gas flow passage R 1 , and thereby enable more efficient heating of the water. Therefore energy efficiency can be further improved.
  • FIG. 13 is a horizontal sectional view of the schematic configuration of a small boiler B 104 according to the present embodiment.
  • the small boiler B 104 according to the present embodiment is such that the first pipe 1 is configured in a star shape that is curved toward the combustion gas flow passage R 1 and the water flow passage R 3 at a fixed interval.
  • the formation of the first pipe 101 into a star shape which is curved at a fixed interval enables an increase in the heat exchanging surface area with water W flowing through the water flow passage R 3 and the combustion gas G 2 flowing through the combustion gas flow passage R 1 , and thereby enables more efficient heating of the water.
  • a small boiler was described as an example of a heating apparatus.
  • the present invention is not limited in this regard, and may be applied to a boiling apparatus for heating water for the purpose of making hot water, or to an apparatus heating oil or gas.
  • the present invention may be applied to a large boiler, or to industrial product such as a fluidized-bed boiler using a heated powder material.
  • the heating apparatus according to the present invention is applied to a recycling fluidized-bed boiler, the particle material may be transported using combustion gas.
  • the external shape and sectional shape of the first pipe 1 and 101 , the second pipe 2 and 102 , the third pipe 3 and 103 , and the fourth pipe 4 and 104 are merely exemplary, and may be configured in an arbitrary manner.
  • a heating apparatus for heating a liquid to be heated enables stabilization of a flame in a combustion chamber and downsizing of the combustion chamber, in addition to improving energy efficiency.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)
  • Gas Burners (AREA)
  • Combustion Of Fluid Fuel (AREA)
US12/919,836 2008-03-04 2009-03-04 Heating apparatus Abandoned US20110005470A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2008-053903 2008-03-04
JP2008053901A JP5211764B2 (ja) 2008-03-04 2008-03-04 加熱装置
JP2008-053901 2008-03-04
JP2008053903A JP5211765B2 (ja) 2008-03-04 2008-03-04 加熱装置
PCT/JP2009/054076 WO2009110509A1 (ja) 2008-03-04 2009-03-04 加熱装置

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US10931107B2 (en) 2016-10-06 2021-02-23 Foresight Energy Ltd. System and method for management of an electricity distribution grid

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JP5453221B2 (ja) 2010-11-18 2014-03-26 国立大学法人東北大学 燃焼実験装置
CN112407346B (zh) * 2020-11-12 2022-07-19 中国空间技术研究院 金属纤维表面燃烧结构热试验方法及装置

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Publication number Priority date Publication date Assignee Title
US20140353975A1 (en) * 2011-09-07 2014-12-04 Eric William Newcomb Efficient thermal hydraulic power generators
US9920648B2 (en) * 2011-09-07 2018-03-20 Eric William Newcomb Concentric three chamber heat exchanger
US10931107B2 (en) 2016-10-06 2021-02-23 Foresight Energy Ltd. System and method for management of an electricity distribution grid

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CN101965481B (zh) 2016-05-04
CA2717301A1 (en) 2009-09-11
BRPI0908046A2 (pt) 2015-08-11
TW200946838A (en) 2009-11-16
EP2253882A4 (en) 2014-02-19
EP2253882B1 (en) 2016-05-25
WO2009110509A1 (ja) 2009-09-11
CA2717301C (en) 2013-07-30
EP2253882A1 (en) 2010-11-24
KR20100120203A (ko) 2010-11-12
RU2010137815A (ru) 2012-04-10
KR101319950B1 (ko) 2013-10-21
CN101965481A (zh) 2011-02-02

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