JP3920843B2 - Water heater - Google Patents

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JP3920843B2
JP3920843B2 JP2003410523A JP2003410523A JP3920843B2 JP 3920843 B2 JP3920843 B2 JP 3920843B2 JP 2003410523 A JP2003410523 A JP 2003410523A JP 2003410523 A JP2003410523 A JP 2003410523A JP 3920843 B2 JP3920843 B2 JP 3920843B2
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hot water
heat exchanger
water
supply
passage
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JP2005172317A (en
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謙二 木村
真二 永田
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Rinnai Corp
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  • Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)

Description

本発明は、給排気管を備え、燃焼ファンにより給排気管を介して燃焼用空気の供給と燃焼排気の排出とを行うようにした給湯器に関する。   The present invention relates to a water heater provided with an air supply / exhaust pipe and configured to supply combustion air and exhaust combustion exhaust through a supply / exhaust pipe by a combustion fan.

本願出願人は、先に、この種の給湯器として、特願２００３−１１３７３４号により、図３に示すようなものを提案している。この先願の給湯器は、ハウジング１と、ハウジング１内に配置した、バーナ２およびバーナ２により加熱される給湯用熱交換器３を収納した燃焼室４と、ハウジング１内に燃焼室４の上方に位置させて配置した、ハウジング１の内部空間に連通する給気室５と、燃焼室４に連通して排気路７を構成する内管６ａと、給気室５に連通して内管６ａとの間に給気路８を構成する外管６ｂとで構成される２重管構造の給排気管６と、外気を給気路８と給気室５とハウジング１の内部空間とを介して燃焼室４に燃焼用空気として供給すると共に、バーナ２の燃焼排気を燃焼室４から排気路７を介して外部に排出する燃焼ファン９とを備える。   The applicant of the present application has previously proposed a water heater of this type as shown in FIG. 3 according to Japanese Patent Application No. 2003-113734. This hot water heater of the prior application includes a housing 1, a combustion chamber 4 that is disposed in the housing 1, and stores a hot water supply heat exchanger 3 that is heated by the burner 2; An air supply chamber 5 communicating with the internal space of the housing 1, an inner pipe 6 a that communicates with the combustion chamber 4 and constitutes the exhaust passage 7, and an inner pipe 6 a that communicates with the air supply chamber 5. The air supply / exhaust pipe 6 having a double-pipe structure composed of the outer pipe 6b constituting the air supply path 8 therebetween, and the outside air through the air supply path 8, the air supply chamber 5, and the internal space of the housing 1 And a combustion fan 9 for supplying the combustion exhaust from the burner 2 to the outside through the exhaust passage 7 from the combustion chamber 4 while supplying the combustion chamber 4 with combustion air.

ところで、上記の如き２重管構造の給排気管６を使用すると、排気路７を流れる高温の燃焼排気によって給気路８を流れる空気が７０〜１００℃程度まで加熱されることがある。このままでは、ハウジング１内に高温空気が流入することになり、燃焼ファン９やハウジング１内に設ける制御ユニット１０が昇温して、その作動不良や誤作動をきたすおそれがある。   By the way, when the supply / exhaust pipe 6 having the double pipe structure as described above is used, the air flowing through the supply path 8 may be heated to about 70 to 100 ° C. by high-temperature combustion exhaust gas flowing through the exhaust path 7. If this is the case, high-temperature air will flow into the housing 1, and the temperature of the combustion fan 9 or the control unit 10 provided in the housing 1 may rise, resulting in malfunction or malfunction.

そこで、先願のものでは、給気室５に、給湯用熱交換器３の上流側の給水路１１から分岐して給湯用熱交換器３の下流側の出湯路１２に合流するバイパス通路１３に介設される冷却用熱交換器１４を配置し、給気室５に流入した高温空気をバイパス通路１３に流れる冷水と冷却用熱交換器１４で熱交換させて冷却するようにしたものを提案している。   Therefore, in the prior application, a bypass passage 13 branched into the air supply chamber 5 from the upstream water supply passage 11 of the hot water supply heat exchanger 3 and joined to the hot water supply passage 12 downstream of the hot water supply heat exchanger 3. The cooling heat exchanger 14 interposed between the cooling water and the cooling air exchanger 14 is cooled by cooling the hot air flowing into the air supply chamber 5 with the cooling water flowing in the bypass passage 13 and the cooling heat exchanger 14. is suggesting.

ところで、冷却用熱交換器を具備しない給湯器であるが、従来、バイパス通路と出湯路の合流部を、バイパス通路と給水路の分岐部よりも鉛直方向上方に位置させて、冷水サンドイッチ現象の発生を防止するようにしたものが知られている(例えば、特許文献１参照)。冷水サンドイッチ現象は、出湯停止時に、バイパス通路と給水路の分岐部から給湯用熱交換器→バイパス通路と出湯路の合流部→バイパス通路の経路で分岐部に戻る閉ループ内の温水と冷水が両者の比重差により閉ループ内で回転するように流動し、バイパス通路内の冷水が合流部から給湯用熱交換器側に逆流して、給湯用熱交換器と合流部との間の出湯路の部分に冷水が滞留し、再出湯時にこの冷水が流出する現象である。   By the way, although it is a water heater without a heat exchanger for cooling, conventionally, the merging portion of the bypass passage and the hot water passage is positioned vertically above the branch portion of the bypass passage and the water supply passage, A device that prevents generation is known (for example, see Patent Document 1). The cold water sandwich phenomenon is that when hot water is stopped, hot water and cold water in the closed loop that returns to the branching section through the bypass passage and the heat exchanger for hot water supply → the junction of the bypass path and the hot water path from the branching section of the bypass passage and the water supply path are both Part of the hot water supply path between the hot water heat exchanger and the merging part, the cold water in the bypass passage flows back to the hot water heat exchanger side from the merging part. This is a phenomenon in which cold water stays in the water and flows out when the hot water is discharged again.

これを更に詳述するに、上記閉ループを、その鉛直方向最高位置と鉛直方向最低位置とを互いに逆向き結ぶ第１と第２の２つの流路に二分し、第１流路内と第２流路内の任意の高さｙにおける滞留水の比重を夫々ρ１，ρ２とし、第１流路と第２流路の最低位置から最高位置までの滞留水の比重の鉛直方向の積分値を夫々∫ρ１ｄｙ，∫ρ２ｄｙと定義する。各流路の滞留水の鉛直方向積分値∫ρ１ｄｙ，∫ρ２ｄｙに重力加速度を乗じた値は、閉ループの最低位置における各流路の水圧に等しくなる。そのため、∫ρ１ｄｙ＝∫ρ２ｄｙになるように滞留水が流動する。   More specifically, the closed loop is divided into two first and second flow paths that connect the highest vertical position and the lowest vertical position in opposite directions, and the first and second flow paths are divided into two. The specific gravity of the stagnant water at an arbitrary height y in the flow path is defined as ρ1 and ρ2, respectively, and the vertical integrated values of the specific gravity of the stagnant water from the lowest position to the highest position of the first flow path and the second flow path are respectively shown. ∫ρ1dy and ∫ρ2dy are defined. The values obtained by multiplying the vertical integral values ∫ρ1dy and ∫ρ2dy of the accumulated water in each flow path by gravity acceleration are equal to the water pressure of each flow path at the lowest position of the closed loop. Therefore, the staying water flows so that ∫ρ1dy = ∫ρ2dy.

バイパス通路と出湯路の合流部は、一般的に、バイパス通路と給水路の分岐部と鉛直方向同一高さに位置している。この場合、第１流路が閉ループの鉛直方向最高位置たる給湯用熱交換器の出口部から合流部とバイパス通路とを介して閉ループの鉛直方向最低位置たる分岐部に至る流路、第２流路が給湯用熱交換器の出口部から給湯用熱交換器を介して分岐部に至る流路であるとすると、分岐部とその上方の給湯用熱交換器の入口部との間の給水路の部分(第２流路の一部分)に滞留する冷水の影響で∫ρ１ｄｙ＜∫ρ２ｄｙになる。そのため、第２流路内の滞留水が分岐部を介して第１流路側に流動し、バイパス通路内の冷水が合流部から給湯用熱交換器側に流れて、冷水サンドイッチ現象が発生する。   The junction of the bypass passage and the hot water outlet is generally located at the same height in the vertical direction as the branch portion of the bypass passage and the water supply passage. In this case, the first flow path is a flow path from the outlet portion of the hot water heat exchanger, which is the highest position in the vertical direction of the closed loop, to the branch portion, which is the lowest position in the vertical direction of the closed loop, via the merge portion and the bypass passage. If the channel is a flow path from the outlet of the hot water supply heat exchanger to the branch through the hot water heat exchanger, the water supply path between the branch and the inlet of the hot water heat exchanger above it ∫ρ1dy <∫ρ2dy due to the influence of the cold water staying in the portion (part of the second flow path). Therefore, the stagnant water in the second flow path flows to the first flow path side through the branching section, and the cold water in the bypass passage flows from the joining section to the hot water supply heat exchanger side, and a cold water sandwich phenomenon occurs.

これに対し、バイパス通路と出湯路の合流部を、バイパス通路と給水路の分岐部よりも鉛直方向上方に位置させれば、バイパス通路に滞留する冷水の影響で第１流路の滞留水の比重積分値∫ρ１ｄｙが増加し、第２流路から第１流路への分岐部を介しての滞留水の流動が抑制されて、冷水サンドイッチ現象の発生も抑制される。   On the other hand, if the junction of the bypass passage and the hot water passage is positioned vertically above the branch portion of the bypass passage and the water supply passage, the accumulated water in the first flow path is affected by the cold water remaining in the bypass passage. The specific gravity integral value ∫ρ1dy increases, the flow of the staying water through the branch from the second flow path to the first flow path is suppressed, and the occurrence of the cold water sandwich phenomenon is also suppressed.

然し、上記先願の冷却用熱交換器１４を具備する給湯器において、上記図３に示されているように、バイパス通路１３と出湯路１２の合流部１３ｂを、バイパス通路１３と給水路１１の分岐部１３ａよりも鉛直方向上方に位置させると、出湯停止時に、給湯用熱交換器３で後沸きされた高温の湯が冷却用熱交換器１４に移行し、再出湯時に出湯温度が高温化する不具合を生ずる。   However, in the water heater provided with the cooling heat exchanger 14 of the prior application, as shown in FIG. 3, the junction 13 b of the bypass passage 13 and the outlet 12 is connected to the bypass passage 13 and the water supply passage 11. If the hot water hot water boiled in the hot water supply heat exchanger 3 is transferred to the cooling heat exchanger 14 when the hot water is stopped, the hot water temperature is high when the hot water is discharged again. Cause problems.

図４は、図３のＡ〜Ｄの各点、即ち、出湯路１２の合流部１３ｂ下流のＡ点、バイパス通路１３の合流部１３ｂ近傍のＢ点、冷却用熱交換器１４の中間のＣ点、バイパス通路１３の分岐部１３ａ近傍のＤ点で計測した水温を示している。ｔ１は出湯を停止した時点、ｔ２は出湯を再開した時点であり、出湯停止から再開までの時間は１分間である。尚、出湯時は、出湯路１２の合流部１３ｂ下流の水温が４０℃になるように制御し、また、出湯停止後に燃焼ファン９の継続作動で５秒間のアフターパージを行っている。図４に示されているように、出湯を停止した瞬間にＢ点の温度が急上昇する。これは、慣性により出湯路１２の温水が合流部１３ｂからバイパス通路１３に流入したためと考えられる。尚、図３の分岐部１３ａと合流部１３ｂとの高さの差の実際値は２ｃｍである。   4 shows points A to D in FIG. 3, that is, point A downstream of the junction 13 b of the outlet 12, point B near the junction 13 b of the bypass passage 13, and C in the middle of the cooling heat exchanger 14. The water temperature measured at point D in the vicinity of the point, the branch portion 13a of the bypass passage 13 is shown. t1 is the time when hot water is stopped, t2 is the time when hot water is restarted, and the time from the hot water stop to restart is 1 minute. In addition, at the time of hot water discharge, control is performed so that the water temperature downstream of the junction 13b of the hot water passage 12 becomes 40 ° C., and after the hot water is stopped, the combustion fan 9 is continuously operated to perform after purge for 5 seconds. As shown in FIG. 4, the temperature at point B rapidly rises at the moment when the hot water is stopped. This is presumably because the hot water in the hot water outlet 12 flows into the bypass passage 13 from the junction 13b due to inertia. Note that the actual value of the difference in height between the branching portion 13a and the merging portion 13b in FIG. 3 is 2 cm.

ここで、出湯停止時には、分岐部１３ａから給湯用熱交換器３→合流部１３ｂ→冷却用熱交換器１４の経路で分岐部１３ａに戻る閉ループ内で滞留水が流動可能になる。そして、閉ループの鉛直方向最高位置は冷却用熱交換器１４の最高部、閉ループの鉛直方向最低位置は分岐部１３ａになり、また、閉ループの最高位置と最低位置とを互いに逆向きに結ぶ２つの流路は、冷却用熱交換器１４の最高部から合流部１３ｂと給湯用熱交換器３とを介して分岐部１３ａに至る第１流路と、冷却用熱交換器１４の最高部から冷却用熱交換器１４を介して分岐部１３ａに至る第２流路とになる。第１流路の滞留水の鉛直方向の比重積分値は、第１流路に給湯用熱交換器が存在し、且つ、合流部１３ｂと最高位置との間のバイパス通路１３の部分に上記の如く温水が流入するため小さくなり、一方、第２流路の滞留水の鉛直方向の比重積分値は、第２流路に滞留するのが殆ど冷水であるため、第１流路の比重積分値に比しかなり大きくなる。その結果、第２流路から分岐部１３ａを介して第１流路に向かう流れを生じ、給湯用熱交換器３内の温水が合流部１３ｂを介して冷却用熱交換器１４に勢い良く流入して、Ｃ点の水温が急上昇し、更に、Ｄ点の温度も上昇する。   Here, when the hot water is stopped, the accumulated water can flow in the closed loop returning from the branch portion 13a to the branch portion 13a through the path of the hot water supply heat exchanger 3 → the merging portion 13b → the cooling heat exchanger 14. The highest vertical position of the closed loop is the highest portion of the heat exchanger 14 for cooling, the lowest vertical position of the closed loop is the branching portion 13a, and the highest position and the lowest position of the closed loop are connected in opposite directions. The flow path is cooled from the highest part of the cooling heat exchanger 14 to the first flow path from the highest part of the cooling heat exchanger 14 to the branching part 13a via the merge part 13b and the hot water supply heat exchanger 3, and from the highest part of the cooling heat exchanger 14. It becomes the 2nd flow path which reaches the branching part 13a via the heat exchanger 14 for an operation. The vertical specific gravity integral value of the stagnant water in the first flow path is the above-described value in the portion of the bypass passage 13 between the junction 13b and the highest position, in which the hot water supply heat exchanger exists in the first flow path. On the other hand, the specific gravity integral value in the vertical direction of the accumulated water in the second flow path is almost constant in the second flow path because of the cold water. It is considerably larger than As a result, a flow from the second flow path toward the first flow path through the branching portion 13a is generated, and the hot water in the hot water supply heat exchanger 3 flows into the cooling heat exchanger 14 through the merging portion 13b. Thus, the water temperature at point C rises rapidly, and the temperature at point D also rises.

このように冷却用熱交換器１４に温水が流入すると、第２流路の比重積分値が減少するが、給湯用熱交換器３内の水温は後沸きにより上昇するため、第１流路の比重積分値は第２流路の比重積分値よりも減少し、給湯用熱交換器３内の温水が合流部１３ｂを介して冷却用熱交換器１４に継続して流入する。その結果、冷却用熱交換器１４内の水温がかなり上昇し、再出湯時に、冷却用熱交換器１４内の温度上昇した温水が合流部１３ｂを介して出湯路１２に流れ、出湯温度が一時的にオーバーシュートする。そして、設定温度(４０℃)に対するオーバーシュート量は１３．５℃程度にもなる。
特許第２６７８３３０号公報(段落００１０〜００１４、図１、図２) When hot water flows into the cooling heat exchanger 14 in this manner, the specific gravity integral value of the second flow path decreases, but the water temperature in the hot water supply heat exchanger 3 rises due to post-boiling, so the first flow path The specific gravity integrated value is smaller than the specific gravity integrated value of the second flow path, and the hot water in the hot water supply heat exchanger 3 continuously flows into the cooling heat exchanger 14 through the junction 13b. As a result, the water temperature in the cooling heat exchanger 14 rises considerably, and the hot water whose temperature in the cooling heat exchanger 14 has risen flows through the junction 13b to the hot water channel 12 at the time of re-heating, so that the hot water temperature temporarily rises. Overshoot. The overshoot amount with respect to the set temperature (40 ° C.) is about 13.5 ° C.
Japanese Patent No. 2678330 (paragraphs 0010 to 0014, FIGS. 1 and 2)

本発明は、以上の点に鑑み、再出湯時の出湯温度のオーバーシュートを抑制できるようにした冷却用熱交換器付きの給湯器を提供することをその課題としている。   This invention makes it the subject to provide the water heater with the heat exchanger for cooling which enabled it to suppress the overshoot of the hot water temperature at the time of re-hot water in view of the above point.

上記課題を解決するために、本発明は、ハウジングと、ハウジング内に配置した、バーナおよびバーナにより加熱される給湯用熱交換器を収納した燃焼室と、ハウジング内に燃焼室の上方に位置させて配置した、ハウジングの内部空間に連通する給気室と、燃焼室に連通して排気路を構成する内管と、給気室に連通して内管との間に給気路を構成する外管とで構成される２重管構造の給排気管と、外気を給気路と給気室とハウジングの内部空間とを介して燃焼室に燃焼用空気として供給すると共に、バーナの燃焼排気を燃焼室から排気路を介して外部に排出する燃焼ファンとを備える給湯器であって、給気室に、給湯用熱交換器の上流側の給水路から分岐して給湯用熱交換器の下流側の出湯路に合流するバイパス通路に介設される冷却用熱交換器を配置するものにおいて、バイパス通路と出湯路の合流部を、バイパス通路と給水路の分岐部よりも鉛直方向下方に位置させることを特徴とする。   In order to solve the above problems, the present invention provides a housing, a combustion chamber disposed in the housing and containing a burner and a heat exchanger for hot water supply heated by the burner, and positioned in the housing above the combustion chamber. An air supply path that communicates with the internal space of the housing, an inner pipe that communicates with the combustion chamber and forms an exhaust path, and an air supply path that communicates with the air supply chamber and forms the air supply path. A double-pipe air supply / exhaust pipe composed of an outer pipe, and external air is supplied as combustion air to the combustion chamber via the air supply path, the air supply chamber, and the internal space of the housing, and the combustion exhaust of the burner And a combustion fan that discharges the air from the combustion chamber to the outside through the exhaust passage, and the supply air chamber is branched from the water supply passage upstream of the hot water supply heat exchanger. Cooling heat exchange installed in a bypass passage that joins the downstream outlet In what place the vessel, the confluence of the bypass passage and hot water passage, characterized in that is positioned vertically below the bifurcation of the bypass passage and the water supply passage.

上記の構成によれば、バイパス通路と給水路の分岐部から給湯用熱交換器→バイパス通路と出湯路の合流部→冷却用熱交換器の経路で分岐部に戻る閉ループの鉛直方向最低位置は合流部になる。そして、閉ループの鉛直方向最高位置と鉛直方向最低位置とを結ぶ互いに逆向きの２つの流路は、最高位置たる冷却用熱交換器の最高部からバイパス通路の下流部分を介して合流部に至る第１流路と、冷却用熱交換器の最高部から冷却用熱交換器とバイパス通路の上流部分と分岐部と給湯用熱交換器と出湯路の上流部分とを介して合流部に至る第２流路とになる。出湯停止時、慣性により出湯路の温水が合流部から第１流路に流入し、第１流路の滞留水の鉛直方向の比重積分値が一時的に減少する。一方、第２流路の滞留水の鉛直方向の比重積分値は、給湯用熱交換器に温水が存在するものの、冷却用熱交換器及び冷却用熱交換器と分岐部との間のバイパス通路の上流部分に存在する冷水の影響で、第１流路の比重積分値よりも大きくなる。そのため、第２流路から合流部を介して第１流路に向かう流れを生じ、給湯用熱交換器内の温水が合流部を経由して冷却用熱交換器に流入する。然し、給湯用熱交換器内の水温が後沸きで上昇すると、第２流路の比重積分値が減少して、遂には第１流路の比重積分値と等しくなり、この時点で第２流路から合流部を介して第１流路に向かう流れが停止する。従って、給湯用熱交換器内の温水が合流部を介して冷却用熱交換器に流入するのは一時的であり、冷却用熱交換器内の水温の上昇が抑制される。その結果、再出湯時の出湯温度のオーバーシュートも抑制される。   According to the above configuration, the lowest position in the vertical direction of the closed loop that returns from the branch portion of the bypass passage and the water supply path to the branch portion in the route of the heat exchanger for hot water supply → the junction of the bypass passage and the hot water passage → the heat exchanger for cooling is Become a confluence. The two mutually opposite flow paths connecting the highest vertical position and the lowest vertical position of the closed loop reach the junction through the downstream portion of the bypass passage from the highest portion of the cooling heat exchanger that is the highest position. The first flow path and the first part from the highest part of the cooling heat exchanger to the junction through the cooling heat exchanger, the upstream part of the bypass passage, the branch part, the hot water supply heat exchanger, and the upstream part of the outlet channel There are two flow paths. When the hot water is stopped, the hot water of the hot water channel flows into the first flow path from the joining portion due to inertia, and the specific gravity integral value in the vertical direction of the accumulated water in the first flow path temporarily decreases. On the other hand, the vertical specific gravity integral value of the stagnant water in the second flow path is a bypass passage between the cooling heat exchanger and the cooling heat exchanger and the branch portion although hot water exists in the hot water supply heat exchanger. It becomes larger than the specific gravity integral value of the first flow path due to the influence of cold water existing in the upstream portion of the first flow path. Therefore, the flow which goes to a 1st flow path from a 2nd flow path via a confluence | merging part arises, and the warm water in the heat exchanger for hot water supply flows into a heat exchanger for cooling via a confluence | merging part. However, when the water temperature in the hot water supply heat exchanger rises after boiling, the specific gravity integral value of the second flow path decreases and finally becomes equal to the specific gravity integral value of the first flow path. The flow from the road toward the first flow path through the junction is stopped. Therefore, it is temporary that the hot water in the hot water supply heat exchanger flows into the cooling heat exchanger via the junction, and the rise in the water temperature in the cooling heat exchanger is suppressed. As a result, overshooting of the hot water temperature at the time of re-hot water is also suppressed.

以下、本発明の実施形態を図面を参照して説明する。図１は本発明の実施形態の給湯器を模式的に示した図、図２は図１の給湯器の各部の水温の変化を示すグラフである。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a diagram schematically showing a water heater according to an embodiment of the present invention, and FIG. 2 is a graph showing changes in the water temperature of each part of the water heater shown in FIG.

図１に示す実施形態の給湯器の基本的な構造は、図３に示した先願の給湯器と同様であり、先願の給湯器と同様な部材には上記と同一の符号を付している。先願の給湯器の説明と重複するが、本実施形態の給湯器の構造を概略的に説明する。   The basic structure of the water heater of the embodiment shown in FIG. 1 is the same as the water heater of the prior application shown in FIG. 3, and the same members as those of the prior application water heater are denoted by the same reference numerals. ing. Although it overlaps with description of the water heater of a prior application, the structure of the water heater of this embodiment is demonstrated roughly.

本実施形態の給湯器は、ハウジング１と、ハウジング１内に配置した略密閉構造の燃焼室４とを備える。燃焼室４には、バーナ２と、バーナ２により加熱される給湯用熱交換器３とが収納されている。ハウジング１内には、更に、燃焼室４の上方に位置させて、ハウジング１の内部空間に連通する給気室５が配置されている。また、家屋の外壁Ｗを通して屋外にのびる給排気管６が設けられている。給排気管６は、燃焼室４に連通して排気路７を構成する内管６ａと、給気室５に連通して内管６ａとの間に給気路８を構成する外管６ｂとから成る二重管構造のものである。そして、ハウジング１内に、燃焼室４の下部に連通する燃焼ファン９を設け、燃焼ファン９により外気を給気路８と給気室５とハウジング１の内部空間とを介して燃焼室４に燃焼用空気として供給すると共に、バーナ２の燃焼排気を燃焼室４から排気路７を介して外部に排出するようにしている。ハウジング１内には、バーナ２及び燃焼ファン９を制御する制御ユニット１０も配置されている。   The water heater according to the present embodiment includes a housing 1 and a combustion chamber 4 having a substantially sealed structure disposed in the housing 1. The combustion chamber 4 houses a burner 2 and a hot water supply heat exchanger 3 heated by the burner 2. An air supply chamber 5 that is located above the combustion chamber 4 and communicates with the internal space of the housing 1 is further disposed in the housing 1. In addition, an air supply / exhaust pipe 6 extending outside through the outer wall W of the house is provided. The supply / exhaust pipe 6 includes an inner pipe 6a that communicates with the combustion chamber 4 and constitutes an exhaust path 7, and an outer pipe 6b that communicates with the supply chamber 5 and constitutes an intake pipe 8a. It has a double tube structure. A combustion fan 9 communicating with the lower part of the combustion chamber 4 is provided in the housing 1, and outside air is supplied to the combustion chamber 4 by the combustion fan 9 via the air supply path 8, the air supply chamber 5, and the internal space of the housing 1. While supplying as combustion air, the combustion exhaust of the burner 2 is discharged | emitted outside from the combustion chamber 4 via the exhaust path 7. FIG. A control unit 10 for controlling the burner 2 and the combustion fan 9 is also arranged in the housing 1.

給湯用熱交換器３には、上流側の給水路１１と下流側の出湯路１２とが接続されている。また、給水路１１から分岐して出湯路１２に合流するバイパス通路１３が設けられている。そして、給気室５に、給気室５とハウジング１の内部空間との連通部となる給気室５の出口部に位置させて、バイパス通路１３に介設される冷却用熱交換器１４を配置している。   An upstream water supply passage 11 and a downstream hot water discharge passage 12 are connected to the hot water supply heat exchanger 3. Further, a bypass passage 13 that branches from the water supply passage 11 and joins the hot water supply passage 12 is provided. Then, the cooling heat exchanger 14 provided in the bypass passage 13 is positioned in the air supply chamber 5 at the outlet of the air supply chamber 5, which serves as a communication portion between the air supply chamber 5 and the internal space of the housing 1. Is arranged.

バーナ２には、火炎を検知するフレームロッド１５と、点火電極１６とが付設されており、また、バーナ２に接続されたガス供給路１７には、上流側から順に、主電磁弁１８と、電磁比例弁１９とが介設されている。給水路１１には、水量センサ２０と電動式の水量調整弁２１とが介設されている。出湯路１２には、バイパス通路１３との合流部１３ｂの下流側に位置させて、出湯温度を検出する湯温サーミスタ２２と、更にその下流側に位置させてリリーフ弁２３とが設けられている。   The burner 2 is provided with a flame rod 15 for detecting a flame and an ignition electrode 16. A gas supply path 17 connected to the burner 2 is provided with a main electromagnetic valve 18, An electromagnetic proportional valve 19 is interposed. A water amount sensor 20 and an electric water amount adjustment valve 21 are interposed in the water supply channel 11. The hot water passage 12 is provided with a hot water temperature thermistor 22 for detecting the hot water temperature positioned downstream of the junction 13b with the bypass passage 13, and a relief valve 23 positioned further downstream thereof. .

出湯路１２の下流端のカラン(図示せず)が開かれて出湯が開始されると、水量センサ２０から通水量に応じて出力される信号を受けて、制御ユニット１０はバーナ２の点火処理を開始する。この点火処理により、燃焼ファン９が駆動されて、給気路６からの外気が給気室５とハウジング１の内部空間とを介して燃焼室４に燃焼用空気として供給される。また、点火電極１６での火花放電が行われると共に、主電磁弁１８が開弁され、更に、電磁比例弁１９が所定開度に開弁されて、バーナ２にガスが供給され、バーナ２に点火される。そして、バーナ２の点火がフレームロッド１５からの信号で確認されると、制御ユニット１０は、湯温サーミスタ２２の検出温度が設定湯温になるように、電磁比例弁１９によるバーナ２の燃焼量の調整と、水量調整弁２１による通水量の調整とを行う。   When a curan (not shown) at the downstream end of the hot water passage 12 is opened and hot water is started, the control unit 10 receives a signal output from the water amount sensor 20 according to the amount of water flow, and the control unit 10 performs an ignition process of the burner 2. To start. By this ignition process, the combustion fan 9 is driven, and the outside air from the air supply path 6 is supplied as combustion air to the combustion chamber 4 through the air supply chamber 5 and the internal space of the housing 1. In addition, spark discharge at the ignition electrode 16 is performed, the main electromagnetic valve 18 is opened, the electromagnetic proportional valve 19 is opened to a predetermined opening, and gas is supplied to the burner 2. Ignited. When the ignition of the burner 2 is confirmed by a signal from the frame rod 15, the control unit 10 determines the amount of combustion of the burner 2 by the electromagnetic proportional valve 19 so that the detected temperature of the hot water thermistor 22 becomes the set hot water temperature. And adjustment of the water flow rate by the water amount adjustment valve 21 are performed.

ところで、バーナ２の燃焼排気は給湯用熱交換器３を流れる水を加熱した後、排気路７を介して外部に排出されるが、この際、排気路７と給気路８との間での熱交換により、給気路８を流れる外気が加熱されて７０〜１００℃程度まで昇温される可能性がある。然し、給気路８から給気室５に流入した高温空気は、給気室５に配置した冷却用熱交換器１４を流れる冷水により冷却される。従って、空気が高温のままハウジング１の内部空間に流入することを防止でき、高温空気による制御ユニット１０や燃焼ファン９の昇温、ひいてはこれらの誤作動等の弊害が防止される。   By the way, the combustion exhaust of the burner 2 heats the water flowing through the hot water supply heat exchanger 3 and is then discharged to the outside through the exhaust path 7. At this time, the exhaust gas between the exhaust path 7 and the air supply path 8 is discharged. As a result of this heat exchange, the outside air flowing through the air supply path 8 may be heated and heated to about 70 to 100 ° C. However, the high-temperature air that has flowed into the supply chamber 5 from the supply passage 8 is cooled by cold water flowing through the cooling heat exchanger 14 disposed in the supply chamber 5. Therefore, air can be prevented from flowing into the internal space of the housing 1 at a high temperature, and adverse effects such as a temperature rise of the control unit 10 and the combustion fan 9 due to the high temperature air and their malfunctions can be prevented.

以上は、上記先願のものと同様であるが、本実施形態では、バイパス通路１３と出湯路１２の合流部１３ｂを、バイパス通路１３と給水路１１の分岐部１３ａよりも鉛直方向下方に位置させており、この点で先願のものと相違する。以下、この相違点による作用効果について詳述する。   Although the above is the same as that of the said prior application, in this embodiment, the confluence | merging part 13b of the bypass channel 13 and the tapping channel 12 is located in the perpendicular direction lower than the branch part 13a of the bypass channel 13 and the water supply channel 11 This is different from the previous application. Hereinafter, the effect by this difference is explained in full detail.

出湯停止時には、分岐部１３ａから給湯用熱交換器３→合流部１３ｂ→冷却用熱交換器１４の経路で分岐部１３ａに戻る閉ループ内で滞留水が流動可能になる。ここで、本実施形態では、閉ループの鉛直方向最低位置は合流部１３ｂになる。そして、閉ループの鉛直方向最高位置と鉛直方向最低位置とを結ぶ互いに逆向きの２つの流路は、最高位置たる冷却用熱交換器１４の最高部からバイパス通路１３の下流部分を介して合流部１３ｂに至る第１流路と、冷却用熱交換器１４の最高部から冷却用熱交換器１４とバイパス通路１３の上流部分と分岐部１３ａと給湯用熱交換器３と出湯路１２の上流部分とを介して合流部１３ｂに至る第２流路とになる。尚、本実施形態では、分岐部１３ａと合流部１３ｂとの高さの差を１０ｃｍに設定している。   When the hot water is stopped, the staying water can flow in the closed loop returning from the branch portion 13a to the branch portion 13a through the path of the hot water supply heat exchanger 3 → the merging portion 13b → the cooling heat exchanger 14. Here, in the present embodiment, the lowest position in the vertical direction of the closed loop is the merging portion 13b. The two flow paths that are opposite to each other and connect the highest vertical position and the lowest vertical position of the closed loop are joined from the highest portion of the cooling heat exchanger 14 that is the highest position via the downstream portion of the bypass passage 13. The first flow path leading to 13b, the upstream portion of the cooling heat exchanger 14, the bypass passage 13 from the highest portion of the cooling heat exchanger 14, the branching portion 13a, the hot water supply heat exchanger 3, and the upstream portion of the outlet 12 The second flow path reaches the merging portion 13b via the. In the present embodiment, the height difference between the branching portion 13a and the merging portion 13b is set to 10 cm.

図２は、図１のＡ〜Ｄの各点、即ち、出湯路１２の合流部１３ｂ下流のＡ点、バイパス通路１３の合流部１３ｂ近傍のＢ点、冷却用熱交換器１４の中間のＣ点、バイパス通路１３の分岐部１３ａ近傍のＤ点で計測した水温を示している。ｔ１は出湯を停止した時点、ｔ２は出湯を再開した時点であり、出湯停止から再出湯までの時間は１分間である。尚、出湯時は、出湯路１２の合流部１３ｂ下流の水温が４０℃になるように制御し、また、出湯停止後に燃焼ファン９の継続作動で５秒間のアフターパージを行っている。   2 shows points A to D in FIG. 1, that is, point A downstream of the junction 13 b of the outlet 12, point B near the junction 13 b of the bypass passage 13, and C in the middle of the cooling heat exchanger 14. The water temperature measured at point D in the vicinity of the point, the branch portion 13a of the bypass passage 13 is shown. t1 is the time when the hot water is stopped, t2 is the time when the hot water is restarted, and the time from the hot water stop to the re-hot water is 1 minute. In addition, at the time of hot water discharge, control is performed so that the water temperature downstream of the junction 13b of the hot water passage 12 becomes 40 ° C., and after the hot water is stopped, the combustion fan 9 is continuously operated to perform after purge for 5 seconds.

図２に示されているように、出湯を停止した瞬間にＢ点の温度が急上昇する。これは、慣性により出湯路１２の温水が合流部１３ｂからバイパス通路１３に流入したためと考えられる。このようにして第１流路の水温が上昇すると、第１流路の滞留水の鉛直方向の比重積分値が一時的に減少する。一方、第２流路の滞留水の鉛直方向の比重積分値は、給湯用熱交換器３に温水が存在するものの、冷却用熱交換器１４及びバイパス通路１３の上流部分に存在する冷水の影響で、第１流路の比重積分値よりも大きくなる。そのため、第２流路から合流部１３ｂを介して第１流路に向かう流れを生じ、給湯用熱交換器３内の温水が合流部１３ｂを経由して冷却用熱交換器１４に流入し、Ｃ点の水温が上昇し、更には、Ｄ点の水温が上昇する。但し、第２流路と第１流路の比重積分値の差は先願のものに比し小さい。そのため、第２流路から合流部１３ｂを介して第１流路に向かう流れの勢いは弱く、Ｃ点、Ｄ点の水温は緩やかに上昇する。   As shown in FIG. 2, the temperature at point B rapidly rises at the moment when the hot water is stopped. This is presumably because the hot water in the hot water outlet 12 flows into the bypass passage 13 from the junction 13b due to inertia. When the water temperature of the first channel rises in this way, the specific gravity integral value in the vertical direction of the accumulated water in the first channel temporarily decreases. On the other hand, the specific gravity integral value in the vertical direction of the stagnant water in the second flow path is influenced by the cold water existing in the upstream portion of the cooling heat exchanger 14 and the bypass passage 13 although hot water is present in the hot water supply heat exchanger 3. Thus, it becomes larger than the specific gravity integral value of the first flow path. Therefore, a flow from the second flow path toward the first flow path via the merge section 13b is generated, and the hot water in the hot water heat exchanger 3 flows into the cooling heat exchanger 14 via the merge section 13b, The water temperature at point C rises, and further, the water temperature at point D rises. However, the difference in specific gravity integral value between the second channel and the first channel is smaller than that of the previous application. For this reason, the momentum of the flow from the second flow path to the first flow path via the merge portion 13b is weak, and the water temperatures at the points C and D gradually rise.

次に、給湯用熱交換器３内の水温が後沸きで上昇すると、第２流路の比重積分値が減少して、遂には第１流路の比重積分値と等しくなり、この時点(図２のｔ３の時点)で第２流路から合流部１３ｂを介して第１流路に向かう流れが停止する。その後は、Ｂ点の水温が放熱で下降し、Ｄ点の水温は上昇しなくなる。尚、Ｃ点の水温は、流動停止後も燃焼室４からの熱伝導により緩やかに上昇しているが、図４に示した先願の給湯器のＣ点の水温に比べるとかなり低い。再出湯時には、出湯温度のオーバーシュートを生ずるが、設定湯温(４０℃)に対するオーバーシュート量は１０．５℃程度であり、オーバーシュート量が１３．５℃にもなる先願の給湯器に比し、３℃も低くなる。   Next, when the water temperature in the hot water supply heat exchanger 3 rises after boiling, the specific gravity integral value of the second flow path decreases and finally becomes equal to the specific gravity integral value of the first flow path. 2 at time t3), the flow from the second flow path to the first flow path via the merge portion 13b stops. Thereafter, the water temperature at point B decreases due to heat dissipation, and the water temperature at point D does not increase. The water temperature at point C rises moderately due to heat conduction from the combustion chamber 4 even after the flow is stopped, but is considerably lower than the water temperature at point C of the prior-art water heater shown in FIG. At the time of re-bathing, an overshoot of the hot water temperature occurs, but the overshoot amount with respect to the set hot water temperature (40 ° C.) is about 10.5 ° C. Compared to 3 ° C.

尚、バイパス通路１３に、給湯用熱交換器３の温水が冷却用熱交換器１４に移行することを阻止する逆止弁を介設することも考えられるが、本実施形態では、合流部１３ｂの位置を分岐部１３ａの位置よりも低くするだけで再出湯時の出湯温度のオーバーシュートを抑制でき、コスト的に非常に有利である。   In addition, although it can also be considered that a bypass valve is provided in the bypass passage 13 to prevent the hot water of the hot water supply heat exchanger 3 from being transferred to the cooling heat exchanger 14, in the present embodiment, the merging portion 13b. It is possible to suppress overshooting of the hot water temperature at the time of re-watering only by making the position of the lower than the position of the branch part 13a, which is very advantageous in terms of cost.

本発明の実施形態の給湯器を模式的に示した図。The figure which showed typically the water heater of embodiment of this invention. 図１の給湯器の各部の水温の変化を示すグラフ。The graph which shows the change of the water temperature of each part of the water heater of FIG. 先願の給湯器を模式的に示した図。The figure which showed typically the water heater of the prior application. 図３の給湯器の各部の水温の変化を示すグラフ。The graph which shows the change of the water temperature of each part of the water heater of FIG.

符号の説明Explanation of symbols

１…ハウジング、２…バーナ、３…給湯用熱交換器、４…燃焼室、５…給気室、６…給排気管、６ａ…内管、６ｂ…外管、７…排気路、８…給気路、９…燃焼ファン、１１…給水路、１２…出湯路、１３…バイパス通路、１３ａ…分岐部、１３ｂ…合流部、１４…冷却用熱交換器。   DESCRIPTION OF SYMBOLS 1 ... Housing, 2 ... Burner, 3 ... Heat exchanger for hot water supply, 4 ... Combustion chamber, 5 ... Air supply chamber, 6 ... Supply / exhaust pipe, 6a ... Inner pipe, 6b ... Outer pipe, 7 ... Exhaust path, 8 ... Air supply path, 9 ... combustion fan, 11 ... water supply path, 12 ... water supply path, 13 ... bypass path, 13a ... branch section, 13b ... merging section, 14 ... cooling heat exchanger.

Claims (1)

ハウジングと、ハウジング内に配置した、バーナおよびバーナにより加熱される給湯用熱交換器を収納した燃焼室と、ハウジング内に燃焼室の上方に位置させて配置した、ハウジングの内部空間に連通する給気室と、燃焼室に連通して排気路を構成する内管と、給気室に連通して内管との間に給気路を構成する外管とで構成される２重管構造の給排気管と、外気を給気路と給気室とハウジングの内部空間とを介して燃焼室に燃焼用空気として供給すると共に、バーナの燃焼排気を燃焼室から排気路を介して外部に排出する燃焼ファンとを備える給湯器であって、
給気室に、給湯用熱交換器の上流側の給水路から分岐して給湯用熱交換器の下流側の出湯路に合流するバイパス通路に介設される冷却用熱交換器を配置するものにおいて、
バイパス通路と出湯路の合流部を、バイパス通路と給水路の分岐部よりも鉛直方向下方に位置させることを特徴とする給湯器。 A housing, a combustion chamber disposed in the housing and containing a burner and a heat exchanger for hot water supply heated by the burner, and a water supply communicating with the interior space of the housing disposed in the housing and positioned above the combustion chamber A double pipe structure comprising an air chamber, an inner pipe communicating with the combustion chamber and constituting an exhaust path, and an outer pipe communicating with the air supply chamber and constituting the air supply path. Supply air as combustion air to the combustion chamber via the air supply / exhaust pipe, the air supply passage, the air supply chamber, and the internal space of the housing, and exhaust the burner combustion exhaust from the combustion chamber to the outside via the exhaust passage. A water heater comprising a combustion fan that
Arranged in the air supply chamber is a cooling heat exchanger that is provided in a bypass passage that branches from the water supply path upstream of the hot water heat exchanger and joins the hot water discharge path downstream of the hot water heat exchanger. In
A hot water heater characterized in that a confluence portion between a bypass passage and a hot water supply passage is positioned vertically below a branch portion between the bypass passage and the water supply passage.
JP2003410523A 2003-12-09 2003-12-09 Water heater Expired - Fee Related JP3920843B2 (en)

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JP2003410523A JP3920843B2 (en) 2003-12-09 2003-12-09 Water heater
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US10612795B2 (en) * 2016-09-14 2020-04-07 Lochinvar, Llc Methods and system for demand-based control of a combination boiler
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DE7737272U1 (en) * 1977-12-07 1983-02-03 Joh. Vaillant Gmbh U. Co, 5630 Remscheid FIREPLACE
JPS59124835U (en) * 1983-02-08 1984-08-22 株式会社ガスタ− Forced air instantaneous water heater
JP2678330B2 (en) * 1992-06-16 1997-11-17 リンナイ株式会社 Bypass mixing type water heater
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JP2001141302A (en) * 1999-11-12 2001-05-25 Rinnai Corp Latent heat recovery type hot water supply apparatus
JP3566615B2 (en) * 2000-02-21 2004-09-15 リンナイ株式会社 Combustion equipment
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