JP3492135B2 - Heat flux meter - Google Patents

Heat flux meter

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Publication number
JP3492135B2
JP3492135B2 JP02889797A JP2889797A JP3492135B2 JP 3492135 B2 JP3492135 B2 JP 3492135B2 JP 02889797 A JP02889797 A JP 02889797A JP 2889797 A JP2889797 A JP 2889797A JP 3492135 B2 JP3492135 B2 JP 3492135B2
Authority
JP
Japan
Prior art keywords
tube
heat
receiving surface
heat receiving
outer frame
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.)
Expired - Fee Related
Application number
JP02889797A
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Japanese (ja)
Other versions
JPH10227703A (en
Inventor
昭一 甲斐
泰雄 早田
八郎 川島
一良 辻岳
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.)
Yamari Industries Ltd
Mitsubishi Heavy Industries Ltd
Original Assignee
Yamari Industries Ltd
Mitsubishi Heavy Industries Ltd
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Application filed by Yamari Industries Ltd, Mitsubishi Heavy Industries Ltd filed Critical Yamari Industries Ltd
Priority to JP02889797A priority Critical patent/JP3492135B2/en
Publication of JPH10227703A publication Critical patent/JPH10227703A/en
Application granted granted Critical
Publication of JP3492135B2 publication Critical patent/JP3492135B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Description

【発明の詳細な説明】 【０００１】 【発明に属する技術分野】本発明は事業用、産業用のボ
イラ、加熱炉等の火炉内熱流束計に関する。 【０００２】 【従来の技術】従来の熱流束計を図５〜図８により説明
する。 【０００３】図５にて、基端閉の筒形の側筒０１の前端
部は径の大きい段差になっており、受熱板０２が挿入さ
れ、溶接ｆされている。また基端中央には穴があり、内
管０６が挿入され、溶接ｆされている。さらに基端周面
には溝があり、外管０４が挿入され、溶接ｆされてい
る。 【０００４】内管０６と外管０４間に、側筒０１の基端
面と所定の距離をあけて、中管０５が同軸に配置されて
いる。 【０００５】受熱板０２は、熱抵抗が大きく、温度差が
えられるよう、熱伝導率の小さいクロメル製である。ま
た側筒０１は、冷却効果を高め、受熱面中央との温度差
を大きくするため、熱伝導率の大きいアルメル製であ
る。 【０００６】内管０６内には２芯線（アルメル０３ａ−
アルメル０３ｂ）のシース管０７が通される。そして、
受熱板０２の中央と、内管０６近くの基端部に小穴があ
けられ、芯線がそれぞれ通され、溶接されている。受熱
板０２と基端部とのメンテナンス空間ａは受熱板０２や
芯線の溶接に必要不可欠である。冷却水は外管０４と中
管０５間から導入され、中管０５と内管０６間からリタ
ーンする。図６に回路図を示す。 【０００７】受熱板０２（クロメル材）と、芯線アルメ
ル０３ａとの溶接により、温度接点ｂの起電力が発生
し、側筒０１（アルメル材）と芯線アルメル０３ｂの溶
接により受熱板０２周囲と側筒０１の溶接部に温度接点
ｃの起電力が発生する。図の様にアルメル線、同志で電
圧０８を計測すれば熱電対の差動式が成立し、受熱板０
２の中央部の温度と受熱板周囲の温度との差、すなわち
温度差の起電力が発生することになる。 【０００８】上記の起電力を計測しても、ボイラ等の熱
流束を直接求めることは出来ない為、起電力と熱量の検
定が必要となる。図７は、検定する場合の概略図を表し
ている。検定は一般に黒体炉３１を用いる。耐火材３３
とヒータ３２からなり、小さな空洞が設けられている。
その空洞部に熱流計３０を挿入して熱量と電圧０８の関
係を得ることができる。熱量は以下のふく射量の計算式
で求められる。 Ｑ＝４．８８×１０-8＊ε1 ＊ε2 （ＴW 4 −ＴH 4 ） Ｋｃａｌ／ｍ2 ｈ ここに、 ε1 ：炉壁面からの放射率（黒体炉でありε1 ＝１） ε2 ：熱流計受熱面０１０の吸収率（通常ε2 ≒１とな
るように面に黒体塗料等を塗布する） ＴW ：炉壁面の絶体温度（°Ｋ） ＴH ：受熱板の絶体温度（°Ｋ）（通常無視出来る） ４．８８×１０-8：ステファンボルツマン常数（Ｋｃａ
ｌ／ｍ2 ｈ°Ｋ） すなわち、黒体炉３１の炉壁面の温度と、熱流計３０の
電圧０８を求めることによって、図８に示す様な、縦軸
熱量、横軸電圧にて検定カーブを得ることが出来る。こ
の検定カーブから実際の加熱炉、ボイラ等の熱流束を求
めることが可能となる。 【０００９】 【発明が解決しようとする課題】上記従来の熱流束計の
エレメント部は、構造上及び製作面で下記の問題点があ
った。 受熱板と側筒の溶接において異種金属同志の結合で
あり、熱膨張率が違うため、特に受熱板部で溶接後の冷
却時にクラックが発生し、製作上、歩止まりが悪い。 受熱板及び側筒に起電力を得るため、芯線を穴に挿
入して溶接するが、余りに芯線が細いため溶接不良が発
生する場合もある。 内管と側筒も通常は同様、異種金属の溶接となる
ため、不完全結合となり冷却水の濃洩（極小である
が）、引いては芯線同志に絶縁不良が発生する。 従来のエレメントの構造上、熱電対に用いる材質を
選択すれば、熱流束に対する起電力値を大きく得るため
にも受熱板は熱伝導率が小さいクロメル、側筒は受熱面
の表面温度を小さくするため、熱伝導率が大きいアルメ
ルが通常最適である。しかし、従来の様な構造では、ア
ルメル棒、クロメル棒を加工するため、原材料を特注す
る必要がある。（国外、国内のメーカでも入手が困難） 熱流束計を実際のボイラ等にて挿入して、熱流束を
計測する場合、炉壁面に受熱板をきっちり合せることは
むずかしく、従って余分に炉内に挿入するのが通常であ
るが、側筒の周囲（側面）から熱流束を受け、起電力値
に若干の誤差を発生させる。 メンテナンス空間に若干の水分（受熱板と側筒の溶
接不良から空気が出入りして空気中の水分がいたづらす
るときもある）があれば、絶縁不良の原因となる。 【００１０】本発明は上記問題点を解決することを課題
とする。 【００１１】 【課題を解決するための手段】本発明は上記課題を解決
するため次の手段を講ずる。 【００１２】先端面閉で先端面より小径の筒形の受熱面
筒と、基端閉の筒形で基端に上記受熱面筒の外径に同じ
径の穴を持つとともに内径が同受熱面筒の先端面の外径
に同じ外枠管と、上記受熱面筒の基端につながれる内管
と、上記外枠管の基端につながれる外管と、上記内管お
よび外管間に配置される中管と、上記受熱面筒の先端面
中央に穴をあけ先端部が挿入されるとともに固着される
シース管型の第１の熱電対と、上記受熱面筒の側面に径
方向の穴をあけ先端部が挿入されるとともに固着される
シース管型の第２の熱電対とを有し、上記受熱面筒は外
枠管内に挿入され、かつ同受熱面筒、外枠管および上記
シース管は同一材料製である。 【００１３】以上において、先端部が計測対象の火炉内
に挿入される。そして、外管と中管間に冷却水が導入さ
れ、先端部で中管と内管間からリターンされる。すると
受熱面筒の先端面は熱負荷を直接受けるため、高い温度
になり、その側面は外枠管で熱遮へいされるとともに基
端部は冷却されるので大きい温度傾斜がえられる。これ
らは第１の熱電対と第２の熱電対により検出され、火炉
内の熱流束が算出される。 【００１４】このようにして、構成が簡単であるので小
型化できる。受熱面筒、外枠管およびシース管が同一材
料であるため、固着性がよく、かつそれぞれの固着部の
熱応力が減少し、接続部の耐久性が大幅に向上する。 【００１５】 【発明の実施の形態】本発明の実施の一形態を図１〜図
４により説明する。 【００１６】図１と図２にて、受熱面筒２は先端面閉
で、筒部は先端面より小径の筒形になっている。また基
端部は外周面が削られている。外枠管３は基端閉の筒形
で、内径が受熱面筒２の先端面の外形と同一であり、基
端面に受熱面筒２の筒の外径と同径の穴があけられてい
る。そして受熱面筒２は外枠管３内に挿入され溶接ｆさ
れる。 【００１７】内管６は受熱面筒２の基端部に挿入され溶
接される。また外枠管３の基端部外周面は削られ、外管
４の先端部に挿入され溶接される。さらに内管６と外管
４間に中管５が配置される。 【００１８】受熱面筒２の先端面中央には穴ｄがあけら
れ、図３に示すようなシース管０７型のアルメル線０３
ａ、クロメル線０３ｃを持つ第１の熱電対７ａが挿入さ
れ、シース管０７が溶接ｆされる。また受熱面筒２の筒
部には径方向の穴ｅがあけられ同様に第２の熱電対７ｂ
が挿入され、溶接ｆされる。図１図中、８は端末ボック
ス、９は冷却水供給管、１０は冷却水もどし管、１１は
ターミナルボックス、１２はリード線である。 【００１９】なお受熱面筒２、外枠管３、シース管０７
はＳＵＳ製である。熱電対７ａ，７ｂ部の回路図を図４
に示す。熱電対７ａは接地型とし受熱面筒２に接地され
る。熱電対７ｂは非接地型で使用する。これらは差動式
にターミナルボックス１１で結線され、電圧０８はクロ
メル線０３ｃ間で計測される。 【００２０】以上において、先端部が計測対象の火炉内
に挿入される。そして、外管４と中管５間に冷却水が導
入され、先端部で中管と内管間からリターンされる。す
ると受熱面筒２の先端面は熱負荷を直接受けるため、高
温度になり、その側面は外枠管３で熱遮へいされるとと
もに基端部は冷却されるので大きい温度傾斜がえられ
る。これらは熱電対７ａと熱電対７ｂにより検出され、
火炉内の熱流束が算出される。 【００２１】このようにして、構成が簡単であるので小
型化できる。また受熱面筒、外枠管およびシース管が同
一材料であるため、溶接性がよく、かつそれぞれの溶接
部の熱応力が減少し、接続部の耐久性が大幅に向上す
る。 【００２２】熱電対を、差動式として使用するため、従
来例同様の原理で温度差の起電力を得ることが出来る。
さらに絶縁不良が従来例に較べ皆無となる。 【００２３】外枠管３と受熱面筒２の間に空気層ｇを設
置した。これにより外周部からの熱流束の影響を無視出
来るため、計測精度の向上が図れる。また従来例に較べ
筒部に取りつける熱電対７ｂの位置次第で大きな温度
差、すなわち、熱流束に対し、大きな起電力が発生する
ため、計測精度の向上が図れる。 【００２４】 【発明の効果】以上に説明したように、本発明は構成が
簡単であるので、小型化できる。また同一材料製なので
溶接性がよく、耐久性が向上する。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat flux meter in a furnace such as a commercial or industrial boiler or a heating furnace. 2. Description of the Related Art A conventional heat flux meter will be described with reference to FIGS. [0005] In FIG. 5, the front end of a cylindrical side tube 01 whose base end is closed has a step with a large diameter, and a heat receiving plate 02 is inserted and welded. There is a hole in the center of the base end, the inner tube 06 is inserted and welded. Further, there is a groove in the base end peripheral surface, and the outer tube 04 is inserted and welded. A middle tube 05 is coaxially arranged between the inner tube 06 and the outer tube 04 at a predetermined distance from the base end surface of the side tube 01. [0005] The heat receiving plate 02 is made of chromel having a small thermal conductivity so that the thermal resistance is large and a temperature difference can be obtained. The side cylinder 01 is made of alumel having a high thermal conductivity in order to enhance the cooling effect and increase the temperature difference from the center of the heat receiving surface. In the inner tube 06, a two-core wire (Alumel 03a-
A sheath tube 07 of alumel 03b) is passed through. And
A small hole is made in the center of the heat receiving plate 02 and the base end near the inner tube 06, and the core wires are passed through and welded. The maintenance space a between the heat receiving plate 02 and the base end is indispensable for welding the heat receiving plate 02 and the core wire. The cooling water is introduced between the outer pipe 04 and the middle pipe 05, and returns from between the middle pipe 05 and the inner pipe 06. FIG. 6 shows a circuit diagram. [0007] By welding the heat receiving plate 02 (chromel material) and the core wire alumel 03a, an electromotive force at the temperature contact b is generated, and by welding the side tube 01 (alumel material) and the core wire alumel 03b, the periphery of the heat receiving plate 02 is formed. An electromotive force at the temperature contact c is generated at the welded portion of the cylinder 01. As shown in the figure, if the voltage 08 is measured with the alumel wire and the other, the differential type of the thermocouple is established and the heat receiving plate 0
2, a difference between the temperature at the center and the temperature around the heat receiving plate, that is, a temperature difference electromotive force is generated. [0008] Even if the above-mentioned electromotive force is measured, the heat flux of the boiler or the like cannot be directly obtained, so that it is necessary to verify the electromotive force and the amount of heat. FIG. 7 shows a schematic diagram in the case of performing the test. In general, a blackbody furnace 31 is used for the verification. Refractory material 33
And a heater 32, and a small cavity is provided.
The relationship between the calorific value and the voltage 08 can be obtained by inserting the heat flow meter 30 into the cavity. The amount of heat is determined by the following formula for calculating the amount of radiation. Q = 4.88 × 10 -8 * ε 1 * ε 2 (T W 4 -T H 4) Kcal / m 2 h here, epsilon 1: emissivity of the furnace wall (a blackbody furnace epsilon 1 = 1) ε 2: the absorption of the heat flow meter heat receiving surface 010 (typically applying a black coating material or the like on the surface so that ε 2 ≒ 1) T W: furnace wall of absolute body temperature (° K) T H: heat Absolute temperature of plate (° K) (usually negligible) 4.88 × 10 -8 : Stefan Boltzmann constant (Kca
1 / m 2 h ° K) That is, by obtaining the temperature of the furnace wall surface of the black body furnace 31 and the voltage 08 of the heat flow meter 30, the calibration curve is obtained with the vertical axis calorie and the horizontal axis voltage as shown in FIG. Can be obtained. From this verification curve, it is possible to obtain the actual heat flux of the heating furnace, boiler, and the like. [0009] The element portion of the above-mentioned conventional heat flux meter has the following problems in structural and manufacturing aspects. In welding the heat receiving plate and the side tube, dissimilar metals are joined together, and the thermal expansion coefficients are different. Therefore, cracks are generated particularly at the time of cooling after welding in the heat receiving plate portion, and the yield is poor in manufacturing. In order to obtain an electromotive force in the heat receiving plate and the side tube, a core wire is inserted into a hole and welding is performed. However, since the core wire is too thin, poor welding may occur. Similarly, since the inner pipe and the side pipe are usually welded with different kinds of metals, they are incompletely connected and the cooling water leaks (although it is extremely small), and as a result, insulation defects occur between the core wires. In the structure of the conventional element, if the material used for the thermocouple is selected, in order to obtain a large electromotive force value for the heat flux, the heat receiving plate reduces the heat conductivity of the chromel, and the side tube reduces the surface temperature of the heat receiving surface. Therefore, alumel having a large thermal conductivity is usually optimal. However, with a conventional structure, it is necessary to custom order raw materials in order to process alumel bars and chromel bars. (It is difficult for foreign and domestic manufacturers to obtain it.) When measuring the heat flux by inserting a heat flux meter into an actual boiler, etc., it is difficult to fit the heat receiving plate exactly to the furnace wall, so extra It is usually inserted, but it receives a heat flux from the periphery (side surface) of the side tube and generates a slight error in the electromotive force value. If there is a small amount of water in the maintenance space (air may flow in and out due to poor welding between the heat receiving plate and the side tube, the water in the air may fluctuate), causing insulation failure. An object of the present invention is to solve the above problems. The present invention takes the following measures to solve the above-mentioned problems. A heat-receiving surface tube having a cylindrical shape having a closed front end surface and a smaller diameter than the front-end surface, and a heat-receiving surface having an inner diameter equal to the outer diameter of the heat-receiving surface tube at the base end having a base end closed shape. An outer frame tube having the same outer diameter as the outer diameter of the distal end surface of the tube, an inner tube connected to the base end of the heat receiving surface tube, an outer tube connected to the base end of the outer frame tube, and between the inner tube and the outer tube. A middle tube to be disposed, a sheath tube-type first thermocouple into which a hole is drilled at the center of the distal end surface of the heat receiving surface tube, and a distal end portion is inserted and fixed; A sheath tube type second thermocouple to which a hole is drilled and a tip portion is inserted and fixed, wherein the heat receiving surface tube is inserted into the outer frame tube, and the heat receiving surface tube, the outer frame tube, and The sheath tube is made of the same material. In the above, the tip is inserted into the furnace to be measured. Then, cooling water is introduced between the outer pipe and the middle pipe, and is returned from between the middle pipe and the inner pipe at the tip. Then, the distal end face of the heat receiving surface cylinder is directly subjected to a thermal load, so that the temperature becomes high, and the side face is heat shielded by the outer frame pipe and the base end part is cooled, so that a large temperature gradient is obtained. These are detected by the first thermocouple and the second thermocouple, and the heat flux in the furnace is calculated. In this way, the configuration is simple, so that the size can be reduced. Since the heat receiving surface tube, the outer frame tube, and the sheath tube are made of the same material, the fixing property is good, the thermal stress of each fixing portion is reduced, and the durability of the connecting portion is greatly improved. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIGS. In FIGS. 1 and 2, the heat receiving surface cylinder 2 is closed at the distal end surface, and the cylindrical portion has a smaller diameter than the distal end surface. Further, the outer peripheral surface of the base end is shaved. The outer frame tube 3 is a cylindrical tube having a closed base end, the inner diameter is the same as the outer shape of the distal end surface of the heat receiving surface tube 2, and a hole having the same diameter as the outer diameter of the tube of the heat receiving surface tube 2 is formed in the base end surface. I have. Then, the heat receiving surface tube 2 is inserted into the outer frame tube 3 and welded. The inner tube 6 is inserted into the base end of the heat receiving surface tube 2 and welded. Also, the outer peripheral surface of the base end portion of the outer tube 3 is shaved, inserted into the distal end of the outer tube 4 and welded. Further, a middle tube 5 is arranged between the inner tube 6 and the outer tube 4. A hole d is formed at the center of the front end surface of the heat receiving surface tube 2, and a sheath tube 07 type alumel wire 03 as shown in FIG.
a, the first thermocouple 7a having the chromel wire 03c is inserted, and the sheath tube 07 is welded f. A hole e in the radial direction is formed in the cylindrical portion of the heat receiving surface cylinder 2 and the second thermocouple 7b is similarly formed.
Is inserted and welded. In FIG. 1, 8 is a terminal box, 9 is a cooling water supply pipe, 10 is a cooling water return pipe, 11 is a terminal box, and 12 is a lead wire. The heat receiving surface tube 2, outer frame tube 3, sheath tube 07
Is made of SUS. FIG. 4 is a circuit diagram of the thermocouples 7a and 7b.
Shown in The thermocouple 7 a is of a grounding type and is grounded to the heat receiving surface tube 2. The thermocouple 7b is used in a non-grounded type. These are differentially connected by the terminal box 11, and the voltage 08 is measured between the chromel wires 03c. In the above, the tip is inserted into the furnace to be measured. Then, cooling water is introduced between the outer pipe 4 and the middle pipe 5, and is returned from between the middle pipe and the inner pipe at the tip. Then, the distal end surface of the heat receiving surface tube 2 directly receives a thermal load, so that the temperature becomes high. The side surface thereof is thermally shielded by the outer frame tube 3 and the base end portion is cooled, so that a large temperature gradient is obtained. These are detected by the thermocouples 7a and 7b,
The heat flux in the furnace is calculated. In this way, the configuration is simple, so that the size can be reduced. Further, since the heat receiving surface tube, the outer frame tube and the sheath tube are made of the same material, the weldability is good, the thermal stress of each welded portion is reduced, and the durability of the connection portion is greatly improved. Since the thermocouple is used as a differential type, an electromotive force having a temperature difference can be obtained by the same principle as in the conventional example.
Furthermore, there is no insulation failure compared to the conventional example. An air layer g was provided between the outer frame tube 3 and the heat receiving surface tube 2. As a result, the influence of the heat flux from the outer peripheral portion can be ignored, so that the measurement accuracy can be improved. Further, as compared with the conventional example, a large temperature difference, that is, a large electromotive force is generated with respect to the heat flux depending on the position of the thermocouple 7b attached to the cylindrical portion, so that the measurement accuracy can be improved. As described above, the present invention has a simple structure and can be downsized. In addition, since it is made of the same material, the weldability is good and the durability is improved.

【図面の簡単な説明】 【図１】本発明の実施の一形態の部分断面図である。 【図２】同一形態の受熱面筒部の詳細断面図である。 【図３】同一形態の熱電対の断面図である。 【図４】同一形態の回路図である。 【図５】従来例の断面図である。 【図６】同従来例の回路図である。 【図７】同従来例の作用説明図である。 【図８】同従来例の検定カーブ図である。 【符号の説明】 ０１ 側筒 ０１ａ 基板 ０２ 受熱板 ０３ａ，０３ｂ アルメル線 ０３ｃ クロメル線 ０４ 外管 ０５ 中管 ０６ 内管 ０７ シース管 ０８ 電圧計（電圧） ０９ 断熱材 １ 熱流束計 ２ 受熱面筒 ３ 外枠管 ４ 外管 ５ 中管 ６ 内管 ７ａ，７ｂ 熱電対 ８ 端末ボックス ９ 冷却水供給管 １０ 冷却水もどし管 １１ ターミナルボックス １２ リード線 ３０ 熱流束計 ３１ 黒体炉 ３２ ヒータ ３３ 耐火材[Brief description of the drawings] FIG. 1 is a partial sectional view of an embodiment of the present invention. FIG. 2 is a detailed cross-sectional view of a heat receiving surface cylindrical portion having the same configuration. FIG. 3 is a cross-sectional view of a thermocouple of the same embodiment. FIG. 4 is a circuit diagram of the same embodiment. FIG. 5 is a sectional view of a conventional example. FIG. 6 is a circuit diagram of the conventional example. FIG. 7 is an operation explanatory view of the conventional example. FIG. 8 is a diagram showing a test curve of the conventional example. [Explanation of symbols] 01 side tube 01a substrate 02 Heat receiving plate 03a, 03b Alumel wire 03c Chromel wire 04 outer tube 05 medium pipe 06 Inner tube 07 sheath tube 08 Voltmeter (voltage) 09 Insulation 1 heat flux meter 2 Heat receiving tube 3 outer frame pipe 4 outer tube 5 Middle tube 6 Inner tube 7a, 7b thermocouple 8 Terminal box 9 Cooling water supply pipe 10 Cooling water return pipe 11 Terminal box 12 Lead wire 30 heat flux meter 31 Blackbody furnace 32 heater 33 refractory materials

フロントページの続き (72)発明者 川島 八郎 長崎市深堀町五丁目717番１号 三菱重 工業株式会社長崎研究所内 (72)発明者 辻岳 一良 長崎県西彼杵郡香焼町字堀切3021番18号 山里産業株式会社長崎営業所内 (56)参考文献 特開 平８−304185（ＪＰ，Ａ) 実開 昭52−37984（ＪＰ，Ｕ) 実開 昭57−168030（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) G01K 17/08 G01K 7/02 Continuation of the front page (72) Inventor Hachiro Kawashima 5-717-1, Fukahori-cho, Nagasaki-shi Inside the Nagasaki Research Laboratory, Mitsubishi Heavy Industries, Ltd. Nagasaki Sales Office of Yamasato Sangyo Co., Ltd. (56) References JP-A-8-304185 (JP, A) Japanese Utility Model 52-37984 (JP, U) Japanese Utility Model Utility Model 57-168030 (JP, U) (58) Field (Int.Cl. 7 , DB name) G01K 17/08 G01K 7/02

Claims (1)

(57)【特許請求の範囲】 【請求項１】 先端面閉で先端面より小径の筒形の受熱
面筒と、基端閉の筒形で基端に上記受熱面筒の外径に同
じ径の穴を持つとともに内径が同受熱面筒の先端面の外
径に同じ外枠管と、上記受熱面筒の基端につながれる内
管と、上記外枠管の基端につながれる外管と、上記内管
および外管間に配置される中管と、上記受熱面筒の先端
面中央に穴をあけ先端部が挿入されるとともに固着され
るシース管型の第１の熱電対と、上記受熱面筒の側面に
径方向の穴をあけ先端部が挿入されるとともに固着され
るシース管型の第２の熱電対とを有し、上記受熱面筒は
外枠管内に挿入され、かつ同受熱面筒、外枠管および上
記シース管は同一材料製であることを特徴とする熱流束
計。(57) [Claims 1] A tubular heat-receiving surface tube having a closed front end surface and a smaller diameter than the front end surface, and a base-closed cylindrical shape having the same outer diameter as the heat-receiving surface tube at the base end. An outer frame tube having a hole with a diameter and an inner diameter equal to the outer diameter of the distal end surface of the heat receiving surface tube, an inner tube connected to the base end of the heat receiving surface tube, and an outer tube connected to the base end of the outer frame tube A tube, a middle tube disposed between the inner tube and the outer tube, and a sheath-tube-type first thermocouple to which a hole is drilled at the center of the distal end surface of the heat-receiving surface tube, and a distal end portion is inserted and fixed. A second thermocouple of a sheath tube type, which is formed by making a hole in the radial direction on a side surface of the heat-receiving surface tube and having a tip portion inserted and fixed, the heat-receiving surface tube being inserted into an outer frame tube; A heat flux meter, wherein the heat receiving surface tube, the outer frame tube and the sheath tube are made of the same material.
JP02889797A 1997-02-13 1997-02-13 Heat flux meter Expired - Fee Related JP3492135B2 (en)

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