JPS62288446A - Forced combustion type water heater not using heat absorbing fins - Google Patents
Forced combustion type water heater not using heat absorbing finsInfo
- Publication number
- JPS62288446A JPS62288446A JP12820486A JP12820486A JPS62288446A JP S62288446 A JPS62288446 A JP S62288446A JP 12820486 A JP12820486 A JP 12820486A JP 12820486 A JP12820486 A JP 12820486A JP S62288446 A JPS62288446 A JP S62288446A
- Authority
- JP
- Japan
- Prior art keywords
- conical coil
- heat exchanger
- water pipe
- water heater
- winding
- 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.)
- Pending
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 45
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 20
- 239000000567 combustion gas Substances 0.000 claims abstract description 13
- 238000004804 winding Methods 0.000 claims abstract description 12
- 238000010521 absorption reaction Methods 0.000 claims description 4
- 238000009423 ventilation Methods 0.000 claims 1
- 238000004519 manufacturing process Methods 0.000 abstract description 5
- 238000010438 heat treatment Methods 0.000 abstract description 3
- 238000003466 welding Methods 0.000 abstract description 2
- 230000009977 dual effect Effects 0.000 abstract 2
- 238000004299 exfoliation Methods 0.000 abstract 1
- 238000009835 boiling Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000007789 gas Substances 0.000 description 2
- 238000005219 brazing Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 210000003127 knee Anatomy 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000009751 slip forming Methods 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
Classifications
-
- 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
- F24H1/10—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium
- F24H1/12—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium
- F24H1/14—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form
- F24H1/16—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form helically or spirally coiled
- F24H1/165—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium by tubes, e.g. bent in serpentine form helically or spirally coiled using fluid fuel
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)
Abstract
Description
【発明の詳細な説明】
３、発明の詳細な説明
〔産業上の利用分野〕
本発明は、吸熱フィンを用いずに水管を円錐コイル状に
巻回した熱交換器を有する強制燃焼式湯沸器に関するも
のである。Detailed Description of the Invention 3. Detailed Description of the Invention [Field of Industrial Application] The present invention provides a forced combustion water heater having a heat exchanger in which water tubes are wound in a conical coil shape without using heat absorption fins. It is related to vessels.
従来のこの種の強制燃焼式湯沸器は、第４図に示すよう
に、上部の水管にフィンプレート１ａをロウ付けした熱
交換器１の下部にバーナ２を配設して内部を燃焼室３と
しだ内胴４を外胴５により密閉状にとり囲み、その内胴
４と外胴５とめ間に送気路６を形成すると共に、燃焼室
３と送気路６とを内胴４の下部において連通させ、さら
に前記送気路６の上部に送風機７の吐出ロアａを開設し
。As shown in Fig. 4, this type of conventional forced combustion water heater has a heat exchanger 1 with fin plates 1a brazed to the upper water pipe, and a burner 2 disposed at the lower part of the heat exchanger 1 to form a combustion chamber inside. 3 and the inner shell 4 are hermetically surrounded by the outer shell 5, and an air passage 6 is formed between the inner shell 4 and the outer shell 5, and the combustion chamber 3 and the air passage 6 are connected to the inner shell 4. The lower part of the air passage 6 is connected to the air passage 6, and the discharge lower a of the blower 7 is provided at the upper part of the air passage 6.
前記送風機７により吸引された空気を送気路６内に送出
降下させ、前記内胴を冷却した後前記燃焼室３ならびに
バーナ２へ給気する構成のものが実用化されている。A structure in which the air sucked by the blower 7 is sent down into the air passage 6, cools the inner shell, and then is supplied to the combustion chamber 3 and the burner 2 has been put into practical use.
また、水管を円筒コイル状に巻回して熱交換器を構成し
、その円筒コイルを円筒状の遮熱板の内部に挿入すると
共に、上部にバッフルを配設し、これにより吸熱フィン
を使用しない熱交換器を構成することも知られている（
特開昭５９−１７０６４２号公報および特開昭６０−２
３７４７号公報の第１図参照）。In addition, a heat exchanger is constructed by winding water pipes into a cylindrical coil shape, and the cylindrical coil is inserted inside a cylindrical heat shield plate, and a baffle is installed at the top, thereby eliminating the need for heat absorption fins. It is also known to constitute a heat exchanger (
JP-A-59-170642 and JP-A-60-2
(See Figure 1 of Publication No. 3747).
しかし乍ら、第４図に示すように、吸熱フィンを水管に
ロウ付けした熱交換器を使用すると、吸熱フィンの製造
設備およびその吸熱フィンをロウ付けするための設備が
必要となるばかりでなく、吸熱フィン使用のために熱容
量が大きくなって後沸き現象が発生し、そのための対策
を必要とするなど、熱交換器製造のコストが嵩むという
問題点がある。However, as shown in Figure 4, using a heat exchanger in which heat absorbing fins are brazed to water pipes not only requires equipment for manufacturing the heat absorbing fins and equipment for brazing the heat absorbing fins. However, due to the use of heat-absorbing fins, the heat capacity increases, resulting in an after-boiling phenomenon, which requires countermeasures, which increases the cost of manufacturing the heat exchanger.
また、水管を円筒コイル状に巻回して熱交換器を構成す
る場合には、その円筒コイルを円筒状遮熱板の中に挿入
すると共にその上方内部にバッフルを配設する必要があ
り、この場合、燃焼ガスはバッフルと円筒コイルとの隙
間および円筒コイルと遮熱板との隙間を通って熱交換す
るので、前記双方の隙間を確保するためのスペーサを必
要とし、構造が複雑になると共に、熱交換器の各部の伝
熱量が極端に異なってこれに伴なう種々の障害が生ずる
という問題がある。In addition, when configuring a heat exchanger by winding water pipes into a cylindrical coil, the cylindrical coil must be inserted into a cylindrical heat shield and a baffle must be placed inside the cylindrical heat shield. In this case, the combustion gas exchanges heat through the gap between the baffle and the cylindrical coil and the gap between the cylindrical coil and the heat shield plate, so a spacer is required to secure the gap between the two, which makes the structure complicated and However, there is a problem in that the amount of heat transferred in each part of the heat exchanger is extremely different, resulting in various problems.
本発明は、前記の如き従来技術の問題点を改善し、水管
を円錐コイル状に巻回させるだけで有効な熱交換器を構
成することができ、従って、大がかりな製造設備を必要
とせず、しかも後沸きのない低コストの熱交換器を有す
る強制燃焼式湯沸器を提供することを目的とする。The present invention improves the problems of the prior art as described above, and makes it possible to construct an effective heat exchanger simply by winding water tubes in a conical coil shape.Therefore, large-scale manufacturing equipment is not required. Moreover, it is an object of the present invention to provide a forced combustion type water heater having a low-cost heat exchanger without after-boiling.
本発明は、前記の如き目的を達成せんがため。 The present invention aims to achieve the above objects.
水管を下方から上方に向かってほぼ円錐コイル状に巻上
げると共に、その上端から下方に向かって再びほぼ円錐
コイル状に巻下げた二重円錐コイル部を形成し、かつ、
その二重円錐コイル部の頂部を蓋体により閉塞した熱交
換器を構成し、該熱交換器の内部を燃焼室として円錐コ
イル状の水管と水管との間隙から燃焼ガスを通過させ、
その燃焼ガスの流速を増加させて高い総括伝熱係数が得
られるようにしたことを特徴とする。A double conical coil portion is formed by winding the water tube upward from the bottom into a substantially conical coil shape and then winding it downward again from the upper end into a substantially conical coil shape, and
A heat exchanger is constructed in which the top of the double conical coil portion is closed with a lid, and the inside of the heat exchanger is used as a combustion chamber, and combustion gas is passed through the gap between the conical coil-shaped water tubes.
It is characterized in that a high overall heat transfer coefficient can be obtained by increasing the flow velocity of the combustion gas.
本発明の熱交換器は、前記の如き構成よりなるので、き
わめて簡単な構造で低コストで製造することができ、し
かも、燃焼ガスはすべて円錐コイル状水管の間隙を通過
して排出され、そのコイル間の間隙を例えば２〜４ｍに
設定することにより燃焼ガスの流速を増し、境界層の剥
離現象を起させて高い総括伝熱係数を与えることができ
る。Since the heat exchanger of the present invention has the above-described configuration, it can be manufactured at low cost with an extremely simple structure, and all combustion gas is discharged through the gap between the conical and coiled water tubes. By setting the gap between the coils to, for example, 2 to 4 m, it is possible to increase the flow velocity of the combustion gas and cause a boundary layer separation phenomenon to provide a high overall heat transfer coefficient.
以下１本発明の一実施例を第１図により説明する。 An embodiment of the present invention will be described below with reference to FIG.
第１図において、１′は本発明による熱交換器、２はそ
の下方に配設したバーナ、３は燃焼室、４は内胴、５は
その内胴を密閉状にとり囲む外胴。In FIG. 1, 1' is a heat exchanger according to the present invention, 2 is a burner disposed below the heat exchanger, 3 is a combustion chamber, 4 is an inner shell, and 5 is an outer shell that tightly surrounds the inner shell.
６は内胴４と外胴５との間に形成された送気路で、その
送気路６と燃焼室３とを内胴４の下端において連通させ
ている。７は送風機で、その吐出ロアａを前記送気路６
の上部に開口させている。Reference numeral 6 denotes an air passage formed between the inner shell 4 and the outer shell 5, and communicates the air passage 6 with the combustion chamber 3 at the lower end of the inner shell 4. 7 is a blower, whose discharge lower a is connected to the air supply path 6;
It has an opening at the top.
本発明においては、水管８の入口側８ａの上端に連続し
て下方から上方に向かって円錐コイル状に巻上げた円錐
コイル部８ａ’を形成すると共に、その上端から下方に
向かって前記円錐コイル部８ａ’よりややコイル径の大
きい円錐コイル部８ｂ’を巻下げて形成し、その円錐コ
イル部８ｂ’の下端を水管８の出口側８ｂと接続する。In the present invention, a conical coil portion 8a' is continuously formed at the upper end of the inlet side 8a of the water pipe 8 and is wound up into a conical coil shape from below to above. A conical coil portion 8b' having a slightly larger coil diameter than 8a' is formed by winding down, and the lower end of the conical coil portion 8b' is connected to the outlet side 8b of the water pipe 8.
この場合、各円錐コイル部８ ａ’ 、 ８ ｂ’の水
管の間隔Ｑは、後述の如く１強制燃焼に際し、燃焼ガス
の流速を増して高い総括伝熱係数が得られるように２〜
４ｍとする。なお、水管の直径は１０〜１４＋ａである
。すなわち、Ｑが前記より大きすぎると燃焼ガスの流速
を増すことができないので熱交換効率が悪くなり、小さ
すぎると送風機の能力が大きいものを必要とするので好
ましくない。In this case, the interval Q between the water tubes of each conical coil portion 8a', 8b' is set to 2 to 2 to increase the flow rate of combustion gas and obtain a high overall heat transfer coefficient during forced combustion as described later.
The length shall be 4m. Note that the diameter of the water tube is 10 to 14+a. That is, if Q is too large, the flow rate of the combustion gas cannot be increased, resulting in poor heat exchange efficiency, and if it is too small, a blower with high capacity is required, which is not preferable.
なお、上記の記述は、便宜上、円錐コイル部８ａ’を巻
上げると共に、その外側の円錐コイル部８ｂ’を巻下げ
ると表現したが、実際に製造する際には、入口側の水管
８ａの上端に円錐コイル部８ａ’を形成しておき、また
、出口側の水管８ｂの上端に円錐コイル部８ｂ’を形成
しておき、その各円錐コイル部８ ａ’ 、 ８ ｂ’
を頂部において溶接により接合するものである。Note that in the above description, for convenience, the conical coil portion 8a' is wound up and the outer conical coil portion 8b' is unwound, but in actual manufacturing, the upper end of the water pipe 8a on the inlet side is A conical coil part 8a' is formed at the upper end of the water pipe 8b on the outlet side, and a conical coil part 8b' is formed at the upper end of the water pipe 8b on the outlet side, and each of the conical coil parts 8a', 8b'
are joined by welding at the top.
このようにして二重円錐コイル状の熱交換器を形成して
その内部を燃焼室３となし、かつ、その二重円錐コイル
の頂部を耐熱性の蓋体９で閉塞する。なお、図中１０は
器体で、水管８の入口側８ａおよび出口側８ｂは器体外
において水道管ならびに給湯配管に接続されている。４
ａは排気口、１１はガス配管、１２はガス弁である。In this way, a double conical coil-shaped heat exchanger is formed, the inside of which serves as a combustion chamber 3, and the top of the double conical coil is closed with a heat-resistant lid 9. In addition, in the figure, 10 is a container body, and the inlet side 8a and outlet side 8b of the water pipe 8 are connected to a water pipe and a hot water supply pipe outside the container body. 4
a is an exhaust port, 11 is a gas pipe, and 12 is a gas valve.
本発明の強制燃焼式湯沸器は、前記の如く、二重円錐コ
イル状であって、その上部からの燃焼ガスの通過を蓋体
により抑えた構造の熱交換器となしたので、燃焼ガスは
すべてのコイルの間を均等に通るようになり、コイル間
の間隔ａを２〜４Ｉにすることにより、燃焼ガスの流速
を増し、境界層の剥雛現象を起して高い総括伝熱係数を
得ることができる。これは、裸管群で構成された熱交換
器から定量的に求められる。すなわち。As mentioned above, the forced combustion type water heater of the present invention is a heat exchanger having a structure in which the combustion gas is prevented from passing through from the upper part of the heat exchanger, which is in the shape of a double conical coil, and the passage of combustion gas from the upper part of the heat exchanger is suppressed. passes through all the coils equally, and by setting the spacing a between the coils to 2 to 4I, the flow velocity of the combustion gas is increased and the boundary layer peeling phenomenon occurs, resulting in a high overall heat transfer coefficient. can be obtained. This can be quantitatively determined from a heat exchanger made up of bare tubes. Namely.
インプット Ｉ ５＝３０，０００ ｋｃａｌ／ｈ
ｒアウトプット Ｑ。＝２５，０００ ｋｃａＱ／ｈ
ｒ理論火炎温度 Ｔ工＝１，７８８℃
排気温度 Ｔ、：２８０℃
伝熱面積 Ａ ＝０．３５＋ｏ”
入水温 ｔ １：１６．８℃
出湯温 ｔ、＝５６．８℃
（Ｔニーｔｔ） （Ｔｌ ｔｔ）
平均対数温度差 ΔＴｍ＝□
Ｉ ｎ（（Ｔｘ−ｔ Ｊ／ （Ｔｔ ｔ １））＝６
９９．０℃
Ｑｏ＝ Ａ−ΔＴ ｍ−Ｕより総括伝熱係数Ｕは１０２
ｋｃａＡ／ｈｒ−ｍ”Ｃである。Input I 5=30,000 kcal/h
r output Q. =25,000 kcaQ/h
rTheoretical flame temperature T = 1,788℃ Exhaust temperature T: 280℃ Heat transfer area A = 0.35+o'' Inlet water temperature t 1: 16.8℃ Output water temperature t, = 56.8℃ (T knee tt) (Tl tt) Average logarithmic temperature difference ΔTm=□ I n ((Tx-t J/ (Tt t 1))=6
From 99.0℃ Qo=A-ΔT m-U, the overall heat transfer coefficient U is 102
kcaA/hr-m''C.
これに対し、従来のフィンプレートを用いた熱交換器は
。In contrast, conventional heat exchangers using fin plates.
インプット Ｉ ５＝３０，０００ ｋｃａｕ／ｈ
ｒアウトプット Ｑｏ：＝２５，０００ ｋｃａｌ／
ｈｒ理論火炎温度 Ｔよ＝１，７８８℃
排気温度 Ｔ ２＝ ２１ｏ℃ −伝熱面積
Ａ ＝０．７２２ｍ”
入水温 ｔ １＝＝ １６．０℃出湯温
ｔ、＝５６．０℃
で、上記と同様に計算してΔＴｍは７０３℃であるから
、Ｕは４９ ｋｃａｌＬ／ｈｒ−ｍ”Ｃとなり、伝熱面
積を約１７２に縮小しても従来のフィンプレートを用い
た熱交換器と同等ないしそれ以上の熱交換を行なうこと
ができる。Input I 5=30,000 kcau/h
r output Qo:=25,000 kcal/
hr Theoretical flame temperature T = 1,788℃ Exhaust temperature T 2 = 21o℃ - Heat transfer area
A = 0.722m” Inlet water temperature t 1== 16.0℃ Output water temperature
t, = 56.0℃, calculated in the same way as above, ΔTm is 703℃, so U is 49 kcalL/hr-m"C, and even if the heat transfer area is reduced to about 172, the conventional fin It can perform heat exchange equivalent to or better than a heat exchanger using plates.
さらに、本発明によれば１円錐コイル部を巻上げと巻下
げの内外二重としたので、熱交換部分の高さを低くおさ
えて各部の伝熱量をほぼ均等化することができる。さら
に、本発明は前記の如くフィンプレートがないので、熱
容量を低くおさえて後沸きの発生を防止することができ
る。Further, according to the present invention, since one conical coil portion has double winding and winding inside and outside, the height of the heat exchange portion can be kept low and the amount of heat transferred to each portion can be made almost equal. Furthermore, since the present invention does not have a fin plate as described above, the heat capacity can be kept low and the occurrence of after-boiling can be prevented.
なお１本発明による熱交換器を使用した場合と。Note that there is one case in which the heat exchanger according to the present invention is used.
従来のフィンプレートを使用した熱交換器を使用した場
合の加熱速度を比較すると、第２図に示すように、従来
は設定温度に達するのにｔ、＝１８秒必要としていたの
に対し、本発明においてはｔ工＝１２秒であった。Comparing the heating speed when using a conventional heat exchanger using fin plates, as shown in Figure 2, the conventional method required t = 18 seconds to reach the set temperature; In the invention, t-t = 12 seconds.
次に、本発明の他の実施例を第３図について説明する。Next, another embodiment of the present invention will be described with reference to FIG.
この実施例は、水管８に連続する円錐コイル部を ８ａ
’−１と ８ａ’−２、および ８ｂ’−１と ８ｂ’
−２との２本に分岐して通水抵抗を小さくすると共に伝
熱面積を大きくしたものである。その他の構成は第１図
に示す実施例と同様であるので、同一部分に同一符号を
付して詳細な説明は省略する。In this embodiment, a conical coil part 8a continuous to the water pipe 8 is
'-1 and 8a'-2, and 8b'-1 and 8b'
-2, which reduces the water flow resistance and increases the heat transfer area. The rest of the structure is the same as that of the embodiment shown in FIG. 1, so the same parts are given the same reference numerals and detailed explanation will be omitted.
前記の各実施例は正円錐コイル部を形成したのを示した
が１本発明は前記の如き正円錐コイル部のみに限定され
るものではない。例えば平面から見て楕円形ないし扁平
角型でその各コーナを円弧で結んだ形にしたほぼ円錐コ
イルにして、燃焼器全体を扁平に構成することもできる
。Although each of the above embodiments has shown that a regular conical coil portion is formed, the present invention is not limited to the regular conical coil portion as described above. For example, the entire combustor can be configured to be flat by using a substantially conical coil that is elliptical or flat square when viewed from above, with each corner connected by an arc.
以上述べたように、本発明によれば、従来のフィンプレ
ートを使用することなく、総括伝熱係数を高めて効果的
な熱交換を行なうことができると共に、後沸きを防止す
ることができる効果がある。As described above, according to the present invention, it is possible to increase the overall heat transfer coefficient and perform effective heat exchange without using conventional fin plates, and the effect is that it is possible to prevent after-boiling. There is.
第１図は本発明の実施の一例を示す断面図、第２図は本
発明と従来例との加熱速度の比較図、第３図は本発明の
他の実施例を示す断面図、第４図は従来例の断面図であ
る。
１′・・・熱交換器、２・・・バーナ、３・・・燃焼室
、４・・・内朋、５・・・外胴、６・・・送気路、７・
・・送風機、８・・・水管、８ａ・・・入口側水管、８
１）・・・出口側水管、８ａ’、 ８ｂ’−円錐コイル
部、８ａ’−１，８ａ’−２゜８ｂ’−１，８ｂ’−２
・・・分岐円錐コイル部。FIG. 1 is a sectional view showing an example of the implementation of the present invention, FIG. 2 is a comparison diagram of heating rates between the present invention and a conventional example, FIG. 3 is a sectional view showing another embodiment of the present invention, The figure is a sectional view of a conventional example. 1'... Heat exchanger, 2... Burner, 3... Combustion chamber, 4... Inner body, 5... Outer shell, 6... Air supply path, 7...
...Blower, 8...Water pipe, 8a...Inlet side water pipe, 8
1)... Outlet side water pipe, 8a', 8b'-conical coil part, 8a'-1, 8a'-2゜8b'-1, 8b'-2
...branched conical coil section.
Claims (1)
を外胴により密閉状にとり囲み、その内胴と外胴との間
に送気路を形成すると共に、その送気路と燃焼室とを内
胴の下端において連通させ、かつ、前記送気路に強制通
気すべくなした強制燃焼式湯沸器において、前記熱交換
器を、下方から上方に向かってほぼ円錐コイル状に巻き
上げると共に、その上端から下方に向かって再びほぼ円
錐コイル状に巻下げた二重円錐コイル部を形成し、かつ
、その二重円錐コイル部の頂部を蓋体により閉塞したも
のにより構成し、前記各円錐コイル状水管の間隙から燃
焼ガスを通過させることによって燃焼ガスの流速を増加
させたことを特徴とする吸熱フィンを用いない強制燃焼
式湯沸器。 ２、円錐コイル部を水管から２本に分岐させて形成した
ことを特徴とする特許請求の範囲第１項に記載の吸熱フ
ィンを用いない強制燃焼式湯沸器。[Claims] 1. A heat exchanger and a burner are disposed in an inner shell, the inner shell is hermetically surrounded by an outer shell, and an air passage is formed between the inner shell and the outer shell. In addition, in a forced combustion water heater in which the air supply passage and the combustion chamber are communicated at the lower end of the inner body, and forced ventilation is provided to the air supply passage, the heat exchanger is arranged from the bottom to the top. A double conical coil portion is formed by winding the coil upwardly into a substantially conical coil shape, and then winding it downward again from the upper end into a substantially conical coil shape, and the top of the double conical coil portion is closed by a lid body. A forced combustion water heater without heat absorption fins, characterized in that the flow rate of the combustion gas is increased by passing the combustion gas through the gaps between the conical and coiled water tubes. 2. The forced combustion water heater without heat absorption fins according to claim 1, wherein the conical coil portion is formed by branching into two from the water pipe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12820486A JPS62288446A (en) | 1986-06-04 | 1986-06-04 | Forced combustion type water heater not using heat absorbing fins |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12820486A JPS62288446A (en) | 1986-06-04 | 1986-06-04 | Forced combustion type water heater not using heat absorbing fins |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62288446A true JPS62288446A (en) | 1987-12-15 |
Family
ID=14979047
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12820486A Pending JPS62288446A (en) | 1986-06-04 | 1986-06-04 | Forced combustion type water heater not using heat absorbing fins |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62288446A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005108876A1 (en) * | 2004-05-11 | 2005-11-17 | Noritz Corporation | Heat exchanger and water heating device |
| CN100445681C (en) * | 2003-04-25 | 2008-12-24 | R·詹诺尼 | Condensation heat exchanger with a gas/air heat collector |
| DE102007026968B4 (en) * | 2006-06-16 | 2012-06-28 | Noritz Corporation | Heat exchanger, water heater and water pipe |
| US8347826B2 (en) | 2006-06-16 | 2013-01-08 | Noritz Corporation | Heat exchanger, water heater and water tube |
| CN107036273A (en) * | 2017-06-22 | 2017-08-11 | 东营市鑫聚合石油科技有限责任公司 | A kind of tower spring formula efficient energy-saving furnace and application method |
-
1986
- 1986-06-04 JP JP12820486A patent/JPS62288446A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100445681C (en) * | 2003-04-25 | 2008-12-24 | R·詹诺尼 | Condensation heat exchanger with a gas/air heat collector |
| WO2005108876A1 (en) * | 2004-05-11 | 2005-11-17 | Noritz Corporation | Heat exchanger and water heating device |
| WO2005108875A1 (en) * | 2004-05-11 | 2005-11-17 | Noritz Corporation | Heat exchanger and water heating device |
| US7428883B2 (en) | 2004-05-11 | 2008-09-30 | Noritz Corporation | Heat exchanger and water heater |
| US7523721B2 (en) | 2004-05-11 | 2009-04-28 | Noritz Corporation | Heat exchanger and water heater |
| DE102007026968B4 (en) * | 2006-06-16 | 2012-06-28 | Noritz Corporation | Heat exchanger, water heater and water pipe |
| US8347826B2 (en) | 2006-06-16 | 2013-01-08 | Noritz Corporation | Heat exchanger, water heater and water tube |
| CN107036273A (en) * | 2017-06-22 | 2017-08-11 | 东营市鑫聚合石油科技有限责任公司 | A kind of tower spring formula efficient energy-saving furnace and application method |
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