EP3150916B1 - Complex heat source apparatus - Google Patents
Complex heat source apparatus Download PDFInfo
- 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
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- 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.)
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- 238000002485 combustion reaction Methods 0.000 claims description 78
- 239000000446 fuel Substances 0.000 claims description 47
- 239000000203 mixture Substances 0.000 claims description 36
- 238000010438 heat treatment Methods 0.000 claims description 25
- 239000007789 gas Substances 0.000 claims description 22
- 239000002737 fuel gas Substances 0.000 claims description 15
- 238000011144 upstream manufacturing Methods 0.000 claims description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 21
- 238000010276 construction Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000003303 reheating Methods 0.000 description 1
- 238000005549 size reduction Methods 0.000 description 1
Images
Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D23/00—Assemblies of two or more burners
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- 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
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- 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
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- 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.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Regulation And Control Of Combustion (AREA)
Description
- 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.
- As this kind of complex heat source apparatus, there is known, e.g., in
JP-A-2006-38423 - According to this arrangement, 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.
- By the way, although not a complex heat source apparatus, there is known, e.g., in
JP-A-2010-151395 - By applying this art to a complex heat source apparatus, the following arrangement is conceivable. That is, 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. Also, 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. At the 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. At the time of single operation, on the other hand, in which only one of the first and the second burners is combusted, only one of the on-off valves corresponding to the valve in question is opened. According to this arrangement, the other heat exchanger corresponding to the burner that is not combusted at the time of single operation can be prevented from being cooled by the air flow from the fan.
- In this case, 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. In this arrangement, however, 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.
- In view of the above-mentioned points, 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.
- In order to solve the above-mentioned problems, 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.
- According to this invention, 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.
- Further, in this invention, at the time of simultaneous operation, when a required combustion amount of the second burner has fallen below a minimum amount of combustion capable of continuous combustion of the second burner, 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. According to this arrangement, even if the upper limit amount of combustion of the second burner is limited below the rated amount of combustion at the time of simultaneous operation, the lower limit amount of combustion of the second burner can be made lower, by the on-off control, than the minimum amount of combustion that is capable of continuous combustion. The reduction in the turndown ratio can be prevented.
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FIG. 1 is a schematic sectional view showing the complex heat source apparatus according to an embodiment of this invention. -
FIG. 2 is a graph showing variable ranges of amounts of combustion of the first burner and the second burner at the time of respective operations. - A complex heat source apparatus according to an embodiment of this invention as shown in
FIG. 1 is made up of: a first heat exchanger 11 for hot water supply; a second heat exchanger 12 for space heating; a first burner 21 for heating the first heat exchanger 11; and a second burner 22 for heating the second heat exchanger 12. - Each of the first and the second burners 21, 22 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-shapedburner body 21, and is disposed in a posture facing downward with thecombustion plate 22 lying on the lower side. Each of first and second combustion boxes 31, 32 that enclose the combustion space at the lower side of each of the first and second burners 21, 22 is disposed so as to house therein each of the first and second heat exchangers 11, 12, respectively. Further, there is provided anexhaust duct 4 which is in communication with the lower ends of both the first and second combustion boxes 31, 32. It is thus so arranged that the combustion exhaust gases from each of the first and second burners 21, 22 can flow through each of the first and second heat exchangers 11, 12 to theexhaust duct 4. - By the way, since hot water supply requires a larger heating capacity than space heating, the first burner 21 is arranged to be a large burner having a larger rated combustion amount (maximum combustion amount) than the second burner 22. Further, the
exhaust duct 4 is partitioned by apartition plate 41 disposed therein into a duct portion through which the combustion exhaust gases from the first burner 21 flow and the other duct portion through which the combustion exhaust gases from the second burner 22 flow. - Each of the first and second heat exchangers 11, 12 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 ofFIG. 1 ; and a snakingheat absorbing tube 12 which penetrates through theseheat absorbing fins 11. Although not illustrated, theheat absorbing tube 12 of the first heat exchanger 11 has connected thereto a water supply pipe on an upstream side and a hot water delivery pipe on the downstream side. It is thus so arranged that, when a hot water faucet on the downstream side of the hot water delivery pipe is opened to let the water flow to the first heat exchanger 11, the first burner 21 is combusted, so that hot water at a set temperature is delivered from the hot water faucet. Although not illustrated, theheat absorbing tube 12 of the second heat exchanger 12 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 12. - Further, the first and second burners 21, 22 have connected thereto a common
air supply passage 5. Thisair supply passage 5 has interposed therein asingle fan 6 which supplies primary air. To that portion of theair supply passage 5 which is on an upstream side of thefan 6 is connected agas outlet 71 which is on a downstream end of agas supply passage 7 for supplying fuel gas. That portion of the of theair supply passage 5 to which thegas 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 amain valve 72, and a zerogovernor 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 thefan 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. - Further, the first connection portion 521 connecting the first burner 21 and the
air supply passage 5 together is provided with a first on-off valve 81. The second connection portion 522 connecting the second burner 22 and theair supply passage 5 together is provided with a second on-off valve 82. The first on-off valve 81 and the second on-off valve 82 are respectively driven by anactuator 81 such as an electromagnetic solenoid, and the like. - At the time of single operation of hot water supply in which only the first burner 21 is combusted to thereby heat the first heat exchanger 11, the first on-off valve 81 is opened to feed the air-fuel mixture to the first burner 21 and, at the same time, the second on-off valve 82 is closed to stop the air-fuel mixture supply to the second burner 22. Further, in order for the amount of the air-fuel mixture supply to the first burner 21 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. In addition, at the time of single operation of space heating in which only the second burner 22 is combusted to thereby heat the second heat exchanger 12, the second on-off valve 82 is opened to feed the air-fuel mixture to the second burner 22 and, at the same time, the first on-off valve 81 is closed to stop the air-fuel mixture supply to the first burner 21. Further, in order for the amount of the air-fuel mixture supply to the second burner 22 to become a value corresponding to the space heating demand combustion amount (amount of combustion required for supplying the hot water of a set temperature to the heating circuit), adjustment is made by the rotational speed of thefan 6. - With reference to
FIG. 2 , at the time of single operation of hot water supply, the amount of combustion of the first burner 21 is made variable with the hot water demand combustion amount between the rated combustion amount Qmax1 of the first burner 21 and the minimum combustion amount capable of performing continuous combustion thereof (lower limit of combustion amount free from back firing) Qminii. At the time of single operation of space heating, the amount of combustion of the second burner 22 is made variable with the space heating demand combustion amount between the rated combustion amount Qmax2 of the second burner 22 and the minimum combustion amount Qmini1 capable of continuous combustion. - At the time of simultaneous operation of hot water supply and space heating by combusting the first burner 21 to heat the first heat exchanger 11 and also by combusting the second burner 22 to heat the second heat exchanger 12 respectively, priority is given to the hot water supply in a state in which both the first and the second on-off valves 81, 82 are left open. In this manner, adjustment is made by the number of rotation of the
fan 6 so that the amount of the air-fuel mixture supply to the first burner 21 becomes the value corresponding to the hot water demand combustion amount. Here, at the time of simultaneous operation, if setting is made such that the amount of the air-fuel mixture supply to the second burner 22 becomes a maximum amount corresponding to the rated combustion amount Qmax2 of the second burner 22 in a state in which the amount of air-fuel mixture supply to the first burner 21 becomes a maximum amount corresponding to the rated combustion amount Qmax1 of the first burner 21, it becomes necessary to enlarge the size of thefan 6 so as to correspond to the maximum value of a total amount of the air-fuel mixture supply. In addition, the noises of the fan at the time of simultaneous operation become larger. - As a solution, in this embodiment, the following arrangement has been made. That is, the second connection portion 522 is provided with a
resistance portion 53. In a state in which, at the time of simultaneous operation, the amount of the air-fuel mixture supply to the first burner 21 becomes a maximum amount, setting is made so that the amount of air-fuel mixture supply to the second burner 22 becomes smaller than the maximum amount corresponding to the rated combustion amount Qmax2. According to this arrangement, since the maximum value of the amount of the total air-fuel mixture supply is reduced, the size reduction of thefan 6 as well as the reduction in the noises at the time of simultaneous operation can be attained. - The second on-off valve 82 may be arranged to be of a needle-valve construction so that, even in an opened state of the second on-off valve 82, the second connection portion 522 can be adequately throttled, whereby the flow resistance through the second connection portion 522 can be set as described above.
- In case the flow resistance through the second connection portion 522 is set in the above-mentioned manner, as shown in
FIG. 2 , the upper limit combustion amount Qmax2' of the second burner 22 at the time of simultaneous operation becomes lower than the rated combustion amount Qmax2. As a result, the turn down ratio of the second burner 22 at the time of simultaneous operation will become smaller if no measure is taken. - As a solution, in this embodiment, in case the required amount of combustion of the second burner 22 at the time of simultaneous operation falls below the minimum amount of combustion Qmin2 that is capable of continuous combustion of the second burner 22, an on-off control is performed in which the second on-off valve 82 is opened or closed so that the second burner 22 is intermittently combusted in an amount of combustion above the minimum amount of combustion Qmin2. According to this arrangement, even if the upper-limit amount of combustion Qmax2' of the second burner 22 is limited below the rated combustion amount Qmax2 at the time of simultaneous combustion, the lower limit combustion amount of combustion Qmin2' of the second burner 22 can be made lower, by means of the on-off control, than the minimum amount of combustion Qmin2 that is capable of continuous combustion. As a result, the turn down ratio of the second burner 22 can be prevented from becoming small.
- Description has so far been made of the embodiment of this invention with reference to the drawings. This invention, however, shall not be limited to the above, but the following arrangement may be employed. For example, a venturi portion is provided in that portion of the
air supply passage 5 which is on the downstream side of thefan 6. The downstream end of thegas supply passage 7 is connected to the venturi portion. Then a zero governor, which adjusts the secondary gas pressure to an equal pressure as the outlet pressure of thefan 6, may be interposed in thegas supply passage 7 as the flow amount adjusting means. In this case, the differential pressure between the outlet pressure of thefan 6 and the venturi portion is proportional to the amount of the primary air supply by thefan 6. The amount of the fuel gas supply will also be proportional to the amount of the primary air supply. - Further, it is also possible to interpose a proportional valve, as the flow control means, in the
gas supply passage 7 in order to make adjustments with the proportional valve so that the amount of the fuel gas supply is proportional to the amount of the primary air supply. In this case, the downstream end of the gas supply passage may be connected to either of an upstream portion and a downstream portion of the fan in theair supply passage 5. Further, 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 11 is for supplying hot water, and the second heat exchanger 12 is for space heating. However, this invention can similarly be applicable to the one in which the second heat exchanger 12 is used other than for space heating such as for reheating a bath tab. -
- 11
- first heat exchanger
- 12
- second heat exchanger
- 21
- first burner
- 22
- second burner
- 5
- air supply passage
- 521
- first connection portion
- 522
- second connection portion
- 6
- fan
- 7
- gas supply passage
- 71
- gas outlet (downstream end of the gas supply passage)
- 73
- zero governor (flow control means)
- 81
- first on-off valve
- 82
- second on-off valve
Claims (2)
- A complex heat source apparatus comprising:first and second, i.e., a total of two, heat exchangers (11, 12);a first burner (21) for heating the first heat exchanger (11);a second burner (22) for heating the second heat exchanger (12) in which the first burner (21) is larger in rated amount of combustion than the second burner (22), both the first and the second burners (21, 22) being constituted by totally aerated combustion burners;first and second combustion boxes (31, 32) that enclose a combustion space at the lower side of each of the first and second burners (21, 22), the combustion boxes being disposed so as to house therein the first and second heat exchanger (11, 12) respectivelya single fan (6) for supplying air-fuel mixture or primary air, the fan (6) being interposed in a common air-fuel supply passage (5) connected to both the first and the second burners, a downstream end of a gas supply passage (7) for supplying fuel gas being connected to that portion of the air-fuel supply passage (5) which is on an upstream side or a downstream side of the fan (6), whereby a mixture of the primary air and the fuel gas is supplied through the air-fuel supply passage (5) to both the first and the second burners (21, 22),a flow control means (73) interposed in the gas supply passage (7), said flow control means (73) 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,a first on-off valve (81) disposed at a first connection portion (521) for connecting the air-fuel supply passage (5) and the first burner (21) and a second on-off valve (82) disposed at a second connection portion (522) for connecting the air-fuel supply passage (5) and the second burner (22)wherein the apparatus is adapted suchthat, at a time of simultaneous operation in which both the first and the second burners (21, 22) are combusted, both the first and the second on-off valves (81, 82) are opened and that, at a time of single operation in which only one of the first and the second burners (21, 22) is combusted, only one of the first and the second on-off valves (81, 82) corresponding to said one burner is opened; andthat a flow resistance of the air-fuel mixture at the second connection portion (522) is set such that, in a state in which the amount of air-fuel mixture supply to the first burner (21), at the time of simultaneous operation, becomes a maximum amount corresponding to the rated combustion amount of the first burner (21), the amount of air-fuel mixture supply to the second burner (22) becomes smaller than the maximum amount corresponding to the rated combustion amount of the second burner (22).
- The complex heat source apparatus according to claim 1,
wherein the apparatus is adapted such, that at the time of simultaneous operation, when a required combustion amount of the second burner (22) has fallen below a minimum amount of combustion capable of continuous combustion of the second burner (22), an on-off control is performed in which the second on-off valve (82) is opened or closed to thereby intermittently perform combustion of the second burner (22).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015195646A JP6633335B2 (en) | 2015-10-01 | 2015-10-01 | Combined heat source machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3150916A1 EP3150916A1 (en) | 2017-04-05 |
EP3150916B1 true EP3150916B1 (en) | 2021-01-27 |
Family
ID=57042777
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16191573.1A Active EP3150916B1 (en) | 2015-10-01 | 2016-09-29 | Complex heat source apparatus |
Country Status (2)
Country | Link |
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EP (1) | EP3150916B1 (en) |
JP (1) | JP6633335B2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102020203424B3 (en) * | 2020-03-17 | 2021-07-22 | Dometic Sweden Ab | Heating device and recreational vehicle with heating device |
DE102020203422B4 (en) | 2020-03-17 | 2024-02-01 | Dometic Sweden Ab | Heating device, recreational vehicle with heating device and method for heating fluids in a recreational vehicle |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63213747A (en) * | 1987-03-02 | 1988-09-06 | Noritsu Co Ltd | Hot water supplier |
JPH0646095B2 (en) * | 1987-07-31 | 1994-06-15 | 株式会社ノーリツ | Hot water supply system with heating function |
JPH07117230B2 (en) * | 1987-12-21 | 1995-12-18 | 松下電器産業株式会社 | Gas combustion device |
JP3683400B2 (en) * | 1998-01-23 | 2005-08-17 | リンナイ株式会社 | Combined water heater |
JP3854870B2 (en) * | 2002-01-25 | 2006-12-06 | パロマ工業株式会社 | Combustion device |
JP2006038401A (en) * | 2004-07-29 | 2006-02-09 | Rinnai Corp | Compound heat source machine |
JP4041102B2 (en) | 2004-07-30 | 2008-01-30 | リンナイ株式会社 | 1 can type combined heat source machine |
JP5483049B2 (en) * | 2008-12-25 | 2014-05-07 | 株式会社ノーリツ | Combustion device |
JP2012077964A (en) * | 2010-09-30 | 2012-04-19 | Rinnai Corp | Combustion device |
-
2015
- 2015-10-01 JP JP2015195646A patent/JP6633335B2/en active Active
-
2016
- 2016-09-29 EP EP16191573.1A patent/EP3150916B1/en active Active
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None * |
Also Published As
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EP3150916A1 (en) | 2017-04-05 |
JP2017067410A (en) | 2017-04-06 |
JP6633335B2 (en) | 2020-01-22 |
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