EP3150916B1 - Complex heat source apparatus - Google Patents

Complex heat source apparatus Download PDF

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Publication number
EP3150916B1
EP3150916B1 EP16191573.1A EP16191573A EP3150916B1 EP 3150916 B1 EP3150916 B1 EP 3150916B1 EP 16191573 A EP16191573 A EP 16191573A EP 3150916 B1 EP3150916 B1 EP 3150916B1
Authority
EP
European Patent Office
Prior art keywords
burner
air
combustion
amount
burners
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.)
Active
Application number
EP16191573.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3150916A1 (en
Inventor
Hideo Okamoto
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.)
Rinnai Corp
Original Assignee
Rinnai Corp
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Publication date
Application filed by Rinnai Corp filed Critical Rinnai Corp
Publication of EP3150916A1 publication Critical patent/EP3150916A1/en
Application granted granted Critical
Publication of EP3150916B1 publication Critical patent/EP3150916B1/en
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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
    • F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
    • F23D14/04—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone induction type, e.g. Bunsen burner
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D23/00—Assemblies of two or more burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/02—Regulating fuel supply conjointly with air supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2237/00—Controlling
    • F23N2237/02—Controlling two or more burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2241/00—Applications
    • F23N2241/04—Heating water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2241/00—Applications
    • F23N2241/06—Space-heating and heating water

Definitions

  • the present invention relates to a complex heat source apparatus which is made up of: first and second, i.e., a total of two, heat exchangers; a first burner for heating the first heat exchanger; and a second burner for heating the second heat exchanger, wherein the first burner has a larger rated burning capacity than the second burner.
  • the fan by making the fan to commonly serve both the burners, the costs can be reduced, but the following disadvantages exist. That is, at the time of a single operation in which only one of the first burner and the second burner is combusted to heat one of the heat exchangers corresponding to the said one burner, the air is supplied also to the other of the burners. This air passes, as it is, through the other heat exchanger corresponding to the other of the burners and, as a result, this heat exchanger is cooled. The thermal efficiency of this heat exchanger therefore becomes lower when the heat exchanger is heated again.
  • the gas supply passage has interposed therein a flow control means which enables to vary the fuel gas feed amount in proportion to the amount of primary air supply so as to make the air-fuel ratio of the air-fuel mixture constant. Also the connection portions between each of the burners and the air supply passage are provided with on-off valves.
  • each of the first and the second burners to respectively heat each of the first and the second heat exchangers is constituted by a totally aerated combustion burner.
  • the air-fuel mixture is supplied to both the first and the second burners through an air supply passage in which a single fan is interposed.
  • the first and the second on-off valves are respectively provided at a first connection portion connecting the first burner and the air supply passage and at a second connection portion connecting the second burner and the air supply passage.
  • both the first and the second on-off valves are opened.
  • ordinarily setting is made at the time of simultaneous operation such that, in a state in which the amount of the air-fuel mixture supply to the first burner becomes maximum corresponding to the rated amount of combustion in the first burner, the amount of the air-fuel mixture supply to the second burner also becomes maximum corresponding to the rated combustion amount of the second burner.
  • the fan in order to enable the maximum amounts of air-fuel mixture supply respectively to the first burner and to the second burner at the time of simultaneous operation, the fan must be made larger in capacity. Furthermore, the fan noises at the time of simultaneous operation become large.
  • this invention has a problem of providing a complex heat source apparatus which supplies air-fuel mixture through an air supply passage common to the first and the second burners and in which downsizing of the fan as well as reduction in the noises at the time of the simultaneous operation is possible.
  • this invention has an advantage in providing a complex heat source apparatus comprising: first and second, i.e., a total of two, heat exchangers; a first burner for heating the first heat exchanger; a second burner for heating the second heat exchanger in which the first burner is larger in rated amount of combustion than the second burner, both the first and the second burners being constituted by totally aerated combustion burners; a single fan for supplying air-fuel mixture or primary air, the fan being interposed in a common air-fuel supply passage connected to both the first and the second burners, a downstream end of a gas supply passage for supplying fuel gas being connected to that portion of the air-fuel supply passage which is on an upstream side or a downstream side of the fan, whereby a mixture of the primary air and the fuel gas is supplied through the air-fuel supply passage to both the first and the second burners.
  • a flow control means is interposed in the gas supply passage, the flow control means serving to vary the amount of fuel gas supply in proportion to the amount of primary air supply so that the air-fuel ratio of the air-fuel mixture becomes constant.
  • the complex heat source apparatus comprises first and second combustion boxes that enclose a combustion space at the lower side of each of the first and second burners, the combustion boxes being disposed so as to house therein the first and second heat exchanger respectively.
  • a first on-off valve is disposed at a first connection portion for connecting the air-fuel supply passage and the first burner and a second on-off valve is disposed at a second connection portion for connecting the air-fuel supply passage and the second burner such that, at a time of simultaneous operation in which both the first and the second burners are combusted, both the first and the second on-off valves are opened and that, at a time of single operation in which only one of the first and the second burners is combusted, only one of the first and the second on-off valves corresponding to said one burner is opened.
  • a flow resistance at the second connection portion is set such that, in a state in which the amount of air-fuel mixture supply to the first burner, at the time of simultaneous operation, becomes a maximum amount corresponding to the rated combustion amount of the first burner, the amount of air-fuel mixture supply to the second burner becomes smaller than the maximum amount corresponding to the rated combustion amount of the second burner.
  • the fan in a state in which the amount of the air-fuel mixture supply to the first burner, at the time of simultaneous operation, becomes the maximum amount, the amount of the air-fuel mixture supply to the second burner becomes smaller than the maximum amount. Therefore, the maximum value of the total amount of air-fuel mixture supply will decrease. Accordingly, the fan can be downsized and the noises at the time of simultaneous operation can be reduced.
  • an on-off control is preferably performed in which the second on-off valve is opened or closed to thereby intermittently perform combustion of the second burner.
  • a complex heat source apparatus is made up of: a first heat exchanger 1 1 for hot water supply; a second heat exchanger 1 2 for space heating; a first burner 2 1 for heating the first heat exchanger 1 1 ; and a second burner 2 2 for heating the second heat exchanger 1 2 .
  • Each of the first and the second burners 2 1 , 2 2 is constituted by a totally aerated combustion burner which ejects and combusts air-fuel mixture of fuel gas and primary air through a multiplicity of flame holes (not illustrated) formed in a combustion plate 22 that covers one surface of a box-shaped burner body 21, and is disposed in a posture facing downward with the combustion plate 22 lying on the lower side.
  • Each of first and second combustion boxes 3 1 , 3 2 that enclose the combustion space at the lower side of each of the first and second burners 2 1 , 2 2 is disposed so as to house therein each of the first and second heat exchangers 1 1 , 1 2 , respectively.
  • an exhaust duct 4 which is in communication with the lower ends of both the first and second combustion boxes 3 1 , 3 2 . It is thus so arranged that the combustion exhaust gases from each of the first and second burners 2 1 , 2 2 can flow through each of the first and second heat exchangers 1 1 , 1 2 to the exhaust duct 4.
  • the first burner 2 1 is arranged to be a large burner having a larger rated combustion amount (maximum combustion amount) than the second burner 2 2 .
  • the exhaust duct 4 is partitioned by a partition plate 41 disposed therein into a duct portion through which the combustion exhaust gases from the first burner 2 1 flow and the other duct portion through which the combustion exhaust gases from the second burner 2 2 flow.
  • Each of the first and second heat exchangers 1 1 1 , 1 2 is made up of: a multiplicity of heat absorbing fins 11 which are laminated with one another in the direction perpendicular to the paper surface of FIG. 1 ; and a snaking heat absorbing tube 12 which penetrates through these heat absorbing fins 11.
  • the heat absorbing tube 12 of the first heat exchanger 1 1 has connected thereto a water supply pipe on an upstream side and a hot water delivery pipe on the downstream side.
  • the first burner 2 1 is combusted, so that hot water at a set temperature is delivered from the hot water faucet.
  • the heat absorbing tube 12 of the second heat exchanger 1 2 is connected to the heating circuit of floor heating, and the like through a forward tube and a return tube. Space heating can thus be performed by circulating hot water to the heating circuit through the second heat exchanger 1 2 .
  • first and second burners 2 1 , 2 2 have connected thereto a common air supply passage 5.
  • This air supply passage 5 has interposed therein a single fan 6 which supplies primary air.
  • a gas outlet 71 which is on a downstream end of a gas supply passage 7 for supplying fuel gas. That portion of the of the air supply passage 5 to which the gas outlet 71 is connected is arranged to constitute a venturi portion 51 having a constricted sectional area.
  • the gas supply passage 7 has interposed therein a main valve 72, and a zero governor 73, as a flow control means, which controls the secondary gas pressure to a pressure equivalent to the atmospheric pressure. It means that the amount of fuel gas supply varies with a differential pressure between the atmospheric pressure which is the secondary gas pressure and that suction negative pressure of the fan 6 which operates on the venturi portion 51. Since the suction negative pressure of the fan varies in proportion to the rotational speed of the fan. Therefore, the amount of fuel gas supply varies in proportion to the rotational speed of the fan, i.e., the amount of the primary air supply. The air-fuel ratio of the air-fuel mixture becomes constant.
  • first connection portion 52 1 connecting the first burner 2 1 and the air supply passage 5 together is provided with a first on-off valve 8 1 .
  • the second connection portion 52 2 connecting the second burner 2 2 and the air supply passage 5 together is provided with a second on-off valve 8 2 .
  • the first on-off valve 8 1 and the second on-off valve 8 2 are respectively driven by an actuator 81 such as an electromagnetic solenoid, and the like.
  • the first on-off valve 8 1 is opened to feed the air-fuel mixture to the first burner 2 1 and, at the same time, the second on-off valve 8 2 is closed to stop the air-fuel mixture supply to the second burner 2 2 . Further, in order for the amount of the air-fuel mixture supply to the first burner 2 1 to become a value corresponding to the hot water demand combustion amount (amount of combustion required for supplying the hot water of a set temperature), adjustment is made by the rotational speed of the fan 6.
  • the second on-off valve 8 2 is opened to feed the air-fuel mixture to the second burner 2 2 and, at the same time, the first on-off valve 8 1 is closed to stop the air-fuel mixture supply to the first burner 2 1 .
  • the amount of the air-fuel mixture supply to the second burner 2 2 is made by the rotational speed of the fan 6.
  • the amount of combustion of the first burner 2 1 is made variable with the hot water demand combustion amount between the rated combustion amount Qmax 1 of the first burner 2 1 and the minimum combustion amount capable of performing continuous combustion thereof (lower limit of combustion amount free from back firing) Qminii.
  • the amount of combustion of the second burner 2 2 is made variable with the space heating demand combustion amount between the rated combustion amount Qmax 2 of the second burner 2 2 and the minimum combustion amount Qmini 1 capable of continuous combustion.
  • the second connection portion 52 2 is provided with a resistance portion 53.
  • setting is made so that the amount of air-fuel mixture supply to the second burner 2 2 becomes smaller than the maximum amount corresponding to the rated combustion amount Qmax 2 .
  • the second on-off valve 8 2 may be arranged to be of a needle-valve construction so that, even in an opened state of the second on-off valve 8 2 , the second connection portion 52 2 can be adequately throttled, whereby the flow resistance through the second connection portion 52 2 can be set as described above.
  • an on-off control is performed in which the second on-off valve 8 2 is opened or closed so that the second burner 2 2 is intermittently combusted in an amount of combustion above the minimum amount of combustion Qmin 2 .
  • the lower limit combustion amount of combustion Qmin 2 ' of the second burner 2 2 can be made lower, by means of the on-off control, than the minimum amount of combustion Qmin 2 that is capable of continuous combustion. As a result, the turn down ratio of the second burner 2 2 can be prevented from becoming small.
  • a venturi portion is provided in that portion of the air supply passage 5 which is on the downstream side of the fan 6.
  • the downstream end of the gas supply passage 7 is connected to the venturi portion.
  • a zero governor which adjusts the secondary gas pressure to an equal pressure as the outlet pressure of the fan 6, may be interposed in the gas supply passage 7 as the flow amount adjusting means.
  • the differential pressure between the outlet pressure of the fan 6 and the venturi portion is proportional to the amount of the primary air supply by the fan 6.
  • the amount of the fuel gas supply will also be proportional to the amount of the primary air supply.
  • the above embodiment is a complex heat source apparatus of serving the dual purpose of hot water supply and space heating in which the first heat exchanger 1 1 is for supplying hot water, and the second heat exchanger 1 2 is for space heating.
  • this invention can similarly be applicable to the one in which the second heat exchanger 1 2 is used other than for space heating such as for reheating a bath tab.
EP16191573.1A 2015-10-01 2016-09-29 Complex heat source apparatus Active EP3150916B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2015195646A JP6633335B2 (ja) 2015-10-01 2015-10-01 複合熱源機

Publications (2)

Publication Number Publication Date
EP3150916A1 EP3150916A1 (en) 2017-04-05
EP3150916B1 true EP3150916B1 (en) 2021-01-27

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EP16191573.1A Active EP3150916B1 (en) 2015-10-01 2016-09-29 Complex heat source apparatus

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EP (1) EP3150916B1 (ja)
JP (1) JP6633335B2 (ja)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020203424B3 (de) * 2020-03-17 2021-07-22 Dometic Sweden Ab Heizvorrichtung und Freizeitfahrzeug mit Heizvorrichtung
DE102020203422B4 (de) 2020-03-17 2024-02-01 Dometic Sweden Ab Heizvorrichtung, Freizeitfahrzeug mit Heizvorrichtung und Verfahren zum Heizen von Fluiden in einem Freizeitfahrzeug

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63213747A (ja) * 1987-03-02 1988-09-06 Noritsu Co Ltd 温水給湯器
JPH0646095B2 (ja) * 1987-07-31 1994-06-15 株式会社ノーリツ 暖房機能併設給湯装置
JPH07117230B2 (ja) * 1987-12-21 1995-12-18 松下電器産業株式会社 ガス燃焼装置
JP3683400B2 (ja) * 1998-01-23 2005-08-17 リンナイ株式会社 複合給湯装置
JP3854870B2 (ja) * 2002-01-25 2006-12-06 パロマ工業株式会社 燃焼装置
JP2006038401A (ja) * 2004-07-29 2006-02-09 Rinnai Corp 複合熱源機
JP4041102B2 (ja) 2004-07-30 2008-01-30 リンナイ株式会社 １缶式複合熱源機
JP5483049B2 (ja) * 2008-12-25 2014-05-07 株式会社ノーリツ 燃焼装置
JP2012077964A (ja) * 2010-09-30 2012-04-19 Rinnai Corp 燃焼装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
JP2017067410A (ja) 2017-04-06
JP6633335B2 (ja) 2020-01-22
EP3150916A1 (en) 2017-04-05

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