JP2022147445A - Gas combustor - Google Patents

Gas combustor Download PDF

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JP2022147445A
JP2022147445A JP2021048685A JP2021048685A JP2022147445A JP 2022147445 A JP2022147445 A JP 2022147445A JP 2021048685 A JP2021048685 A JP 2021048685A JP 2021048685 A JP2021048685 A JP 2021048685A JP 2022147445 A JP2022147445 A JP 2022147445A
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Prior art keywords
pipe
gas
bypass pipe
exhaust gas
bypass
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Japanese (ja)
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陽太郎 村上
Yotaro Murakami
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Denso Wave Inc
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Denso Wave Inc
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Priority to JP2021048685A priority Critical patent/JP2022147445A/en
Priority to US17/563,253 priority patent/US20220307725A1/en
Publication of JP2022147445A publication Critical patent/JP2022147445A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/18—Water-storage heaters
    • F24H1/20—Water-storage heaters with immersed heating elements, e.g. electric elements or furnace tubes
    • F24H1/205—Water-storage heaters with immersed heating elements, e.g. electric elements or furnace tubes with furnace tubes
    • 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
    • F23N1/022—Regulating fuel supply conjointly with air supply using electronic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/003—Systems for controlling combustion using detectors sensitive to combustion gas properties
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/18—Water-storage heaters
    • F24H1/186—Water-storage heaters using fluid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/355—Control of heat-generating means in heaters
    • F24H15/36—Control of heat-generating means in heaters of burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/0005—Details for water heaters
    • F24H9/001—Guiding means
    • F24H9/0026—Guiding means in combustion gas channels
    • F24H9/0031—Guiding means in combustion gas channels with means for changing or adapting the path of the flue gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J2215/00—Preventing emissions
    • F23J2215/10—Nitrogen; Compounds thereof
    • 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
    • F23N2900/00—Special features of, or arrangements for controlling combustion
    • F23N2900/05003—Measuring NOx content in flue gas

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chimneys And Flues (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Regulation And Control Of Combustion (AREA)

Abstract

To provide a gas combustor which can be used without placing a high-sensitive gas sensor under a high temperature environment.SOLUTION: A gas water heater 1 is provided with a bypass pipe 15 which is branched from a main pipe 14 of a discharge pipe 13 and in which a flow rate of exhaust gas is set so as to be lower than that in the main pipe 14. A gas sensor 17 is disposed in the bypass pipe 15 and the bypass pipe 15 is cooled by a cooler 18.SELECTED DRAWING: Figure 1

Description

本発明は、ガス燃料を燃焼した際に排ガスを排出する排出管を備えるガス燃焼器に関する。 BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas combustor provided with an exhaust pipe for discharging exhaust gas when burning gas fuel.

例えば給湯器やボイラー等のガス燃焼器については、ＮＯｘやＣＯ２，ＣＯ等の排ガス規制が年々厳しくなっている。例えば、日本におけるボイラー製品には、排ガス中のＮＯｘ濃度を５０ｐｐｍ以下にすることが求められている。排ガス中に含まれるＮＯｘ等の濃度は、燃料の種類や供給量，空気の供給量や大気圧等といった種々のパラメータにより決まるため、様々な条件下において排ガス規制を満たすように燃焼を行うには、排ガス中に含まれているＮＯｘ等の濃度をセンシングして、センシングの結果に応じた燃焼制御を行うことが望ましい。ガスを検出するセンサとしては、例えばジルコニア式や定電位電解方式等のセンサがある。 For gas burners such as water heaters and boilers, for example, regulations on exhaust gases such as NOx, CO 2 , and CO are becoming stricter year by year. For example, boiler products in Japan are required to reduce the NOx concentration in the exhaust gas to 50 ppm or less. The concentration of NOx, etc. contained in the exhaust gas is determined by various parameters such as the type and amount of fuel supplied, the amount of air supplied, and atmospheric pressure. It is desirable to sense the concentration of NOx and the like contained in the exhaust gas and perform combustion control according to the sensing result. As a sensor for detecting gas, there are, for example, a zirconia sensor, a constant potential electrolysis sensor, and the like.

特開２００７－２６３９３３号公報JP 2007-263933 A 特開２０００－７４８７８号公報JP-A-2000-74878

しかしながら、ジルコニア式センサは、測定態様以外のガス成分の影響を受けるため精度が悪く、比較的精度が良い定電位電解方式センサは、電解液を使用しているため高温環境下で使用できないといった問題がある。 However, the zirconia sensor has poor accuracy because it is affected by gas components other than the measurement mode, and the constant potential electrolysis sensor, which has relatively high accuracy, cannot be used in a high temperature environment because it uses an electrolytic solution. There is

本発明は、上記実情に鑑みてなされたものであり、その目的は、精度が良いガスセンサを高温環境下に置くことなく使用できるガス燃焼器を提供することにある。 SUMMARY OF THE INVENTION An object of the present invention is to provide a gas combustor in which a highly accurate gas sensor can be used without placing it in a high-temperature environment.

請求項１記載のガス燃焼器によれば、排出管の主管より分岐し、排ガスの流量が主管よりも少なくなるように設定されるバイパス管を設け、このバイパス管に排ガス中のガスを検出するガスセンサを配置し、冷却機構によってバイパス管を冷却する。このように構成すれば、冷却機構は、排ガスの流量が比較的少ないバイパス管を冷却すれば良いので、小型で低コストのものを用いることができる。これにより、高温環境下では使用できない高精度のガスセンサを使用することが可能になる。 According to the gas combustor of claim 1, a bypass pipe that branches from the main pipe of the exhaust pipe and is set so that the flow rate of the exhaust gas is lower than that of the main pipe is provided, and the gas in the exhaust gas is detected in this bypass pipe. A gas sensor is arranged and a cooling mechanism cools the bypass pipe. With this configuration, the cooling mechanism can cool the bypass pipe through which the flow rate of the exhaust gas is relatively low, so that a compact and low-cost cooling mechanism can be used. This makes it possible to use a highly accurate gas sensor that cannot be used in high temperature environments.

請求項２記載のガス燃焼器によれば、冷却機構を、バイパス管におけるガスセンサの少なくとも上流側に配置する。これにより、排ガスの温度を確実に低下させた状態で、ガスセンサによるセンシングを行わせることができる。 According to the gas combustor of claim 2, the cooling mechanism is arranged at least upstream of the gas sensor in the bypass pipe. As a result, sensing by the gas sensor can be performed while the temperature of the exhaust gas is reliably lowered.

請求項３記載のガス燃焼器によれば、ガス燃料を燃焼することで給水タンク内の水を加熱する構成において、冷却機構を、給水タンクに給水される水を用いて冷却を行う構成とする。すなわち、給水タンクに給水される水を冷媒として用いるので、冷却機構を低コストで構成できる。 According to the gas combustor of claim 3, in the configuration in which the water in the water supply tank is heated by burning the gas fuel, the cooling mechanism is configured to perform cooling using the water supplied to the water supply tank. . That is, since the water supplied to the water supply tank is used as the coolant, the cooling mechanism can be constructed at low cost.

請求項４記載のガス燃焼器によれば、主管内において、バイパス管の入口と出口との間に対応する部位に逆止弁を配置する。排ガスの圧力は、ガス燃料の燃焼状態に応じて変化するが、排ガスの圧力が低い場合は主管内の逆止弁は閉じているので、排ガスは全てバイパス管内に流れる。排ガスの圧力が上昇して逆止弁が開くと、排ガスは主管とバイパス管との双方に流れる。したがって、排ガスの圧力が低い場合でも、ガスセンサによるセンシングを確実に行わせることができる。 According to the gas combustor of claim 4, the check valve is arranged in the portion corresponding to the inlet and outlet of the bypass pipe in the main pipe. The pressure of the exhaust gas changes according to the combustion state of the gas fuel, but when the pressure of the exhaust gas is low, the check valve in the main pipe is closed, so all the exhaust gas flows into the bypass pipe. When the exhaust gas pressure rises and the check valve opens, the exhaust gas flows through both the main pipe and the bypass pipe. Therefore, even when the pressure of the exhaust gas is low, sensing by the gas sensor can be reliably performed.

請求項５記載のガス燃焼器によれば、逆止弁は、バイパス管を流れる排ガスの流量が一定値を超えると開放され、主管及びバイパス管を流れる排ガスの圧力を同一にするように調整されている。このように構成すれば、バイパス管への排ガスの流量を制限して冷却機構による冷却を容易に行うことができると共に、バイパス管の負担を低減できる。 According to the gas combustor of claim 5, the check valve is opened when the flow rate of the exhaust gas flowing through the bypass pipe exceeds a certain value, and is adjusted so that the pressures of the exhaust gas flowing through the main pipe and the bypass pipe are the same. ing. With this configuration, the flow rate of the exhaust gas to the bypass pipe can be restricted to facilitate cooling by the cooling mechanism, and the load on the bypass pipe can be reduced.

第１実施形態であり、ガス燃焼器の一例である本実施形態のガス給湯器の構成を示す図A diagram showing the configuration of a gas water heater of the present embodiment, which is a first embodiment and an example of a gas burner. 図１の排気管部分を拡大して示す図The figure which expands and shows the exhaust pipe part of FIG. ガス給湯器が低火力で運転されている場合の図２相当図Equivalent to Fig. 2 when the gas water heater is operated at low thermal power ガス給湯器が高火力で運転されている場合の図２相当図Equivalent to Fig. 2 when the gas water heater is operated at high thermal power ガス給湯器の運転が停止している状態から開始した場合の各部の変化を示すタイミングチャートTiming chart showing changes in each part when the operation of the gas water heater is started from a stopped state 逆止弁で生じる損失を調整する手法について説明する図Diagram explaining the method of adjusting the loss caused by the check valve 第２実施形態であり、ガス給湯器の構成を示す図2nd Embodiment, the figure which shows the structure of a gas water heater 図７の排気管部分を拡大して示す図The figure which expands and shows the exhaust pipe part of FIG.

（第１実施形態）
以下、第１実施形態について図１から図６を参照して説明する。図１は、ガス燃焼器の一例である本実施形態のガス給湯器１の構成を示す。給湯タンク２の内部には、給水管３を介して図示しない水道より水が給水される。給湯タンク２は、燃焼管４を内蔵しており、燃焼管４の内部でガスの燃焼が行われることで水が加熱されて湯になる。湯は、排出管５を介して外部に供給される。排出管５には、湯の温度を検出するための図示しない温度センサが配置されている。 (First embodiment)
A first embodiment will be described below with reference to FIGS. 1 to 6. FIG. FIG. 1 shows the configuration of a gas water heater 1 of this embodiment, which is an example of a gas burner. Water is supplied to the inside of the hot water supply tank 2 from a tap (not shown) through a water supply pipe 3 . The hot water supply tank 2 incorporates a combustion pipe 4, and gas is burned inside the combustion pipe 4 to heat water into hot water. Hot water is supplied to the outside through the discharge pipe 5 . A temperature sensor (not shown) for detecting the temperature of the hot water is arranged in the discharge pipe 5 .

給湯タンク２には、吸気管６が接続されており、吸気管６の内部にはブロア７が配置されている。ブロア７は、吸気管６の外部にあるコントローラ８により駆動制御され、外部より大気を吸気する。吸気管６の途中部位には、ガス供給管９が比例弁１０を介して接続されている。比例弁１０は、コントローラ８により駆動制御される。これにより、吸気管６内へのガス供給量が調整される。 An intake pipe 6 is connected to the hot water supply tank 2 , and a blower 7 is arranged inside the intake pipe 6 . The blower 7 is driven and controlled by a controller 8 outside the intake pipe 6 and sucks air from the outside. A gas supply pipe 9 is connected to an intermediate portion of the intake pipe 6 via a proportional valve 10 . The proportional valve 10 is driven and controlled by the controller 8 . As a result, the amount of gas supplied to the intake pipe 6 is adjusted.

吸気管６内部のガスと大気との混合気体は、噴射部１２を介して燃焼管４に供給される。燃焼管４内の混合気体は、図示しないイグナイタにより点火されて燃焼される。燃焼管４は、給湯タンク２の図中上部において吸気管６に接続され、給湯タンク２の下方に延びる主部４ａと、給湯タンク２の下方から上方に延びる折返し部４ｂと、そこから主部４ａの周囲を螺旋状に囲んで再び下方に至る螺旋状部４ｃとを備えている。螺旋状部４ｃには排気管１３が接続されており、燃焼後の気体が給湯タンク２の外部に排気される。 A mixture of the gas inside the intake pipe 6 and the atmosphere is supplied to the combustion pipe 4 via the injection part 12 . The mixed gas in the combustion tube 4 is ignited and burned by an igniter (not shown). The combustion pipe 4 is connected to the intake pipe 6 at the upper part of the hot water supply tank 2 in the figure, and has a main portion 4a extending downward from the hot water supply tank 2, a folded portion 4b extending upward from the lower part of the hot water supply tank 2, and a main portion extending therefrom. A spiral portion 4c spirally surrounds the circumference of 4a and extends downward again. An exhaust pipe 13 is connected to the helical portion 4c, and gas after combustion is exhausted to the outside of the hot water supply tank 2. As shown in FIG.

図２にも示すように、排気管１３は、主管１４及びバイパス管１５からなる。バイパス管１５は、主管１４より分岐して排気ガスを流した後に、主管１４に戻して排気させる。バイパス管１５の径断面積は、主管１４よりも小さく設定されている。図２に拡大して示すように、バイパス管１５は、主管１４の下方に接続されるコ字状の配管であり、主管１４への接続箇所が入口１５ａ，出口１５ｂとなっている。そして、主管１４内における入口１５ａと出口１５ｂとの間には、逆止弁１６が配置されている。 As also shown in FIG. 2 , the exhaust pipe 13 consists of a main pipe 14 and a bypass pipe 15 . The bypass pipe 15 branches from the main pipe 14 to flow the exhaust gas, and then returns to the main pipe 14 for exhaust. The diameter cross-sectional area of the bypass pipe 15 is set smaller than that of the main pipe 14 . As shown enlarged in FIG. 2, the bypass pipe 15 is a U-shaped pipe connected to the lower part of the main pipe 14, and has an inlet 15a and an outlet 15b connected to the main pipe 14. As shown in FIG. A check valve 16 is arranged between the inlet 15 a and the outlet 15 b in the main pipe 14 .

バイパス管１５には、排ガス中における例えばＮＯｘ等のガス濃度を検出する、例えば定電位電解方式のガスセンサ１７が配置されている。ガスセンサ１７の上流側には、冷却機構としての冷却器１８が配置されている。冷却器１８は、具体的には図示しないが、例えば冷媒が流れる冷却パイプをバイパス管１５の外周に巻き付けて冷却し、バイパス管１５に流れる排ガスの熱で上昇した冷媒の温度を低下させて、冷却パイプに送出する、という循環を行う構成である。 The bypass pipe 15 is provided with, for example, a constant-potential electrolysis type gas sensor 17 for detecting the concentration of a gas such as NOx in the exhaust gas. A cooler 18 as a cooling mechanism is arranged upstream of the gas sensor 17 . Although not specifically illustrated, the cooler 18 cools the bypass pipe 15 by wrapping a cooling pipe through which the refrigerant flows, for example, around the outer periphery of the bypass pipe 15. It is a configuration that circulates by sending it to a cooling pipe.

コントローラ８は、例えばマイクロコンピュータで構成され、入力部２１，演算部２２及び出力部２３等を備えている。入力部２１は、ガスセンサ１７や温度センサが出力するセンサ信号やを受けて演算部２２に出力する。演算部２２は、入力されるセンサ信号に応じてブロワ７及び比例弁１０を制御する信号を出力部２３を介して出力する。これにより、コントローラ８は、燃焼管４に供給する空気量及びガス燃料の量を制御して、ガス給湯器１の燃焼状態を制御し、湯の温度をユーザにより設定された温度にする。 The controller 8 is composed of, for example, a microcomputer, and includes an input section 21, a calculation section 22, an output section 23, and the like. The input unit 21 receives sensor signals output from the gas sensor 17 and the temperature sensor and outputs them to the calculation unit 22 . The calculation unit 22 outputs a signal for controlling the blower 7 and the proportional valve 10 via the output unit 23 according to the input sensor signal. Thereby, the controller 8 controls the amount of air and gas fuel supplied to the combustion pipe 4, controls the combustion state of the gas water heater 1, and sets the temperature of the hot water to the temperature set by the user.

次に、本実施形態の作用について図３から図５を参照して説明する。図３は、ガス給湯器１の運転状態が低火力であり、排気管１３に流れる排ガスの圧力が比較的低い場合を示している。この時、主管１４にある逆止弁１６は閉じているため、排ガスはバイパス管１５のみに流れる。 Next, the operation of this embodiment will be described with reference to FIGS. 3 to 5. FIG. FIG. 3 shows a case where the operating state of the gas water heater 1 is low thermal power and the pressure of the exhaust gas flowing through the exhaust pipe 13 is relatively low. At this time, since the check valve 16 in the main pipe 14 is closed, the exhaust gas flows only through the bypass pipe 15 .

一方、図４は、ガス給湯器１の運転状態が高火力であり、排気管１３に流れる排ガスの圧力が比較的高い場合を示している。この時、逆止弁１６は開くので、排ガスは主管１４及びバイパス管１５の双方に流れる。図５は、ガス給湯器１の運転状態が図３に示すものから図４に示すものに遷移する場合を示したタイムチャートである。火力が「低」から「高」に変化する間に、閉じていた逆止弁１６が開き始める。すると、主管１４における排ガスの流量は「０」から上昇を開始すると共に、バイパス管１５における排ガスの流量も上昇する。そして、バイパス管１５の流量は、逆止弁１６が全開になる前に頭打ちとなるが、主管１４の流量は逆止弁１６が全開になった時点で一定となる。 On the other hand, FIG. 4 shows a case where the operating state of the gas water heater 1 is high heating power and the pressure of the exhaust gas flowing through the exhaust pipe 13 is relatively high. At this time, the check valve 16 is opened, so the exhaust gas flows through both the main pipe 14 and the bypass pipe 15 . FIG. 5 is a time chart showing a case where the operating state of gas water heater 1 changes from that shown in FIG. 3 to that shown in FIG. The closed check valve 16 begins to open while the heating power changes from "low" to "high". Then, the flow rate of the exhaust gas in the main pipe 14 starts to rise from "0", and the flow rate of the exhaust gas in the bypass pipe 15 also rises. The flow rate of the bypass pipe 15 peaks out before the check valve 16 is fully opened, but the flow rate of the main pipe 14 becomes constant when the check valve 16 is fully opened.

ここで、逆止弁１６が開放された際に、主管１４及びバイパス管１５を流れる排ガスの圧力が同一となるように調整する手法について図６を参照して説明する。各パラメータを以下に示す。
Ａ１：主管１４の配管径
Ａ２: バイパス管１５の配管径
ｖ１：逆止弁１６を閉状態に維持できる最大流量
ｖ２：バイパス管１５に流すことができる最大流量
このとき、
ｖ２＝ｖ１×Ａ１／Ａ２ …（０）
となる。 Here, a method for adjusting the pressure of the exhaust gas flowing through the main pipe 14 and the bypass pipe 15 to be the same when the check valve 16 is opened will be described with reference to FIG. Each parameter is shown below.
A1: Pipe diameter of the main pipe 14 A2: Pipe diameter of the bypass pipe 15 v1: Maximum flow rate that can keep the check valve 16 closed v2: Maximum flow rate that can flow through the bypass pipe 15 At this time,
v2=v1×A1/A2 (0)
becomes.

また、図中に示す配管損失（１）～（３）は、以下になる。
配管損失（１）：主管１４からバイパス管１５への流路が直角に折れ曲がると共に
断面積が変化することによる損失
配管損失（２）：バイパス管１５内の流路が２か所で直角に折れ曲がる
ことによる損失
配管損失（３）：バイパス管１５から主管１４への流路が直角に折れ曲がると共に
断面積が変化することによる損失
尚、バイパス管１５の流路がストレートである部分でも損失は発生するが、僅かであるためここでは無視している。 Piping losses (1) to (3) shown in the figure are as follows.
Piping loss (1): When the flow path from the main pipe 14 to the bypass pipe 15 is bent at right angles,
Loss due to change in cross-sectional area Piping loss (2): The flow path in the bypass pipe 15 bends at two right angles
Loss due to this Piping loss (3): The flow path from the bypass pipe 15 to the main pipe 14 is bent at right angles and
Loss due to change in cross-sectional area Although loss also occurs in the portion where the flow path of the bypass pipe 15 is straight, it is negligible here.

配管損失（１）であるΔＰ１は、（１）式で表される。
ΔＰ１＝０．９４６×ρｖ１２／２＋（１／ＣＣ－１）×ρｖ２２／２ …（１）
尚、「ρ」は水の密度であり、「ＣＣ」は配管径比（Ａ１／Ａ２）で決まる定数である。
配管損失（２）であるΔＰ２は、（２）式で表される。
ΔＰ２＝０．９４６×ρｖ２２／２×２ …（２）
配管損失（３）であるΔＰ３は、（３）式で表される。
ΔＰ３＝（１－Ａ２／Ａ１）×ρｖ２２／２ …（３） ΔP1, which is the pipe loss (1), is represented by the equation (1).
ΔP1=0.946×ρv1 2 /2+(1/C C −1)×ρv2 2 /2 (1)
"ρ" is the density of water, and "C C " is a constant determined by the pipe diameter ratio (A1/A2).
ΔP2, which is the pipe loss (2), is expressed by the equation (2).
ΔP2=0.946×ρv2 2 /2×2 (2)
ΔP3, which is the pipe loss (3), is expressed by the equation (3).
ΔP3=(1−A2/A1)×ρv2 2 /2 (3)

バイパス管１５に流すことができる最大流量ｖ２における圧力損失ＰＬは、上記の損失（１）～（３）の合計となる。
ＰＬ＝ΔＰ１＋ΔＰ２＋ΔＰ３ …（４）
従って、逆止弁１６に、発生する損失が圧力損失ＰＬに等しくなるものを選ぶことで、流量がｖ２を超えた際に逆止弁１６の開放が開始されるようになる。これにより、主管１４及びバイパス管１５を流れる排ガスの圧力が同一となる。 The pressure loss P L at the maximum flow rate v2 that can flow through the bypass pipe 15 is the sum of the above losses (1) to (3).
P L =ΔP1+ΔP2+ΔP3 (4)
Therefore, by selecting the check valve 16 that generates a loss equal to the pressure loss PL , the check valve 16 starts to open when the flow rate exceeds v2. Thereby, the pressure of the exhaust gas flowing through the main pipe 14 and the bypass pipe 15 becomes the same.

以上のように本実施形態によれば、ガス給湯器１において、排出管１３の主管１４より分岐し、排ガスの流量が主管１４よりも少なくなるように設定されるバイパス管１５を設け、バイパス管１５にガスセンサ１７を配置し、冷却器１８によってバイパス管１５を冷却する。このように構成すれば、冷却器１８は、排ガスの流量が比較的少ないバイパス管１５６を冷却すれば良いので、小型で低コストのものを用いることができる。これにより、高温環境下では使用できない高精度のガスセンサ１７を使用することが可能になる。 As described above, according to the present embodiment, in the gas water heater 1, the bypass pipe 15 that branches from the main pipe 14 of the discharge pipe 13 and is set so that the flow rate of the exhaust gas is lower than that of the main pipe 14 is provided. A gas sensor 17 is arranged at 15 and the bypass pipe 15 is cooled by a cooler 18 . With this configuration, the cooler 18 can cool the bypass pipe 156 through which the flow rate of the exhaust gas is relatively low, so that a compact and low-cost cooler can be used. This makes it possible to use a highly accurate gas sensor 17 that cannot be used in high temperature environments.

この場合、冷却器１８を、バイパス管１５におけるガスセンサ１８の上流側に配置することで、排ガスの温度を確実に低下させた状態で、ガスセンサ１８によるセンシングを行わせることができる。 In this case, by arranging the cooler 18 on the upstream side of the gas sensor 18 in the bypass pipe 15, sensing by the gas sensor 18 can be performed while the temperature of the exhaust gas is reliably lowered.

また、主管１４内において、バイパス管１５の入口１５ａと出口１５ｂとの間に対応する部位に逆止弁１６を配置する。排ガスの圧力が低い場合は主管１４内の逆止弁１６は閉じているので、排ガスは全てバイパス管１５に流れるので、ガスセンサ１８によるセンシングを確実に行わせることができる。 In addition, a check valve 16 is arranged in the main pipe 14 at a portion corresponding to the inlet 15 a and the outlet 15 b of the bypass pipe 15 . Since the check valve 16 in the main pipe 14 is closed when the pressure of the exhaust gas is low, all the exhaust gas flows into the bypass pipe 15, so that sensing by the gas sensor 18 can be reliably performed.

更に、逆止弁１６を、バイパス管１５を流れる排ガスの流量が一定値を超えると開放され、主管１４及びバイパス管１５を流れる排ガスの圧力を同一にするように調整する。このように構成すれば、バイパス管への排ガスの流量を制限して冷却機構による冷却を容易に行うことができると共に、バイパス管の負担を低減できる。 Furthermore, the check valve 16 is opened when the flow rate of the exhaust gas flowing through the bypass pipe 15 exceeds a certain value, and the pressure of the exhaust gas flowing through the main pipe 14 and the bypass pipe 15 is adjusted to be the same. With this configuration, the flow rate of the exhaust gas to the bypass pipe can be restricted to facilitate cooling by the cooling mechanism, and the load on the bypass pipe can be reduced.

（第２実施形態）
以下、第１実施形態と同一部分には同一符号を付して説明を省略し、異なる部分について説明する。図７及び図８に示すように、第２実施形態のガス給湯器３１は、給水管３に替わる給水管３２を備えている。給水管３２は、バイパス管１５の下方側に、バイパス管１５に沿うように配設されている。すなわち、第２実施形態では、給水管３２を冷却機構として用いている。 (Second embodiment)
Hereinafter, the same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted, and different parts will be described. As shown in FIGS. 7 and 8, a gas water heater 31 of the second embodiment includes a water supply pipe 32 that replaces the water supply pipe 3. As shown in FIGS. The water supply pipe 32 is arranged below the bypass pipe 15 along the bypass pipe 15 . That is, in the second embodiment, the water supply pipe 32 is used as a cooling mechanism.

給水管３２を流れる水を冷媒として、給水管３２とバイパス管１５との間で熱交換を行い、バイパス管１５の熱を水により奪うことで冷却する。給水管３２は、バイパス管１５に接触するように配置しても良いし、バイパス管１５と給水管３２との間に放熱シートのようなものを介在させて熱交換を行っても良い。これにより、冷却機構を低コストで構成できる。 Using the water flowing through the water supply pipe 32 as a coolant, heat is exchanged between the water supply pipe 32 and the bypass pipe 15, and the heat of the bypass pipe 15 is removed by the water for cooling. The water supply pipe 32 may be arranged so as to be in contact with the bypass pipe 15 , or a heat radiation sheet or the like may be interposed between the bypass pipe 15 and the water supply pipe 32 for heat exchange. As a result, the cooling mechanism can be configured at low cost.

本発明は上記した、又は図面に記載した実施形態にのみ限定されるものではなく、以下のような変形又は拡張が可能である。
冷却器１８を配置する位置は、適宜変更して良い。
ガス給湯器に限ることなく、ガスを燃焼させた際に発生する熱を利用するものであれば適用が可能である。 The present invention is not limited to the embodiments described above or illustrated in the drawings, but can be modified or expanded as follows.
The position where the cooler 18 is arranged may be changed as appropriate.
The present invention is not limited to gas water heaters, and can be applied to any device that utilizes heat generated when gas is burned.

図面中、１はガス給湯器、２は給湯タンク、１３は排気管、１４は主管、１５はバイパス管、１５ａは入口，１５ｂは出口、１６は逆止弁、１７はガスセンサ、１８は冷却器、３１はガス給湯器、３２は給水管を示す。 In the drawing, 1 is a gas water heater, 2 is a hot water tank, 13 is an exhaust pipe, 14 is a main pipe, 15 is a bypass pipe, 15a is an inlet, 15b is an outlet, 16 is a check valve, 17 is a gas sensor, and 18 is a cooler. , 31 indicates a gas water heater, and 32 indicates a water supply pipe.

Claims (5)

ガス燃料を燃焼した際に排ガスを排出する排出管としての主管と、
この主管より分岐して形成され、排ガスの流量が当該排出管よりも少なくなるように設定されるバイパス管と、
このバイパス管に配置され、前記排ガス中のガスを検出するガスセンサと、
前記バイパス管を冷却する冷却機構とを備えるガス燃焼器。 a main pipe as an exhaust pipe for discharging exhaust gas when burning gas fuel;
a bypass pipe formed by branching from the main pipe and set so that the flow rate of the exhaust gas is lower than that of the discharge pipe;
a gas sensor arranged in the bypass pipe for detecting gas in the exhaust gas;
and a cooling mechanism for cooling the bypass pipe. 前記冷却機構を、前記バイパス管における前記ガスセンサの少なくとも上流側に配置する請求項１記載のガス燃焼器。 2. The gas combustor according to claim 1, wherein the cooling mechanism is arranged at least upstream of the gas sensor in the bypass pipe. 水が給水される給水タンクを備え、
前記ガス燃料を燃焼することで前記給水タンク内の水を加熱する構成において、
前記冷却機構は、前記給水タンクに給水される水を用いて冷却を行う請求項２記載のガス燃焼器。 Equipped with a water supply tank to which water is supplied,
In the configuration for heating the water in the water supply tank by burning the gas fuel,
3. The gas combustor according to claim 2, wherein said cooling mechanism performs cooling using water supplied to said water supply tank. 前記主管内において、前記バイパス管の入口と出口との間に対応する部位に配置される逆止弁を備える請求項１から３の何れか一項に記載のガス燃焼器。 4. The gas combustor according to any one of claims 1 to 3, further comprising a check valve arranged in a corresponding portion between an inlet and an outlet of the bypass pipe in the main pipe. 前記逆止弁は、前記バイパス管を流れる排ガスの流量が一定値を超えると開放され、前記主管及び前記バイパス管を流れる排ガスの圧力を同一にするように調整されている請求項４記載のガス燃焼器。 5. The gas according to claim 4, wherein the check valve is opened when the flow rate of the exhaust gas flowing through the bypass pipe exceeds a certain value, and is adjusted so that the pressures of the exhaust gas flowing through the main pipe and the bypass pipe are the same. combustor.
JP2021048685A 2021-03-23 2021-03-23 Gas combustor Pending JP2022147445A (en)

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