JPS61140711A - Multi-holes burner with heat exchanger tube - Google Patents

Abstract

PURPOSE:To spout mixed gas uniformly in the circumferential and axial directions from distribution pipe of mixed gas by installing distribution pipes of sec. air and mixed gas coaxially in such away that many spouting nozzles of mixed gas are protruded on distribution pipe at regular intervals cir cumferentially and axially. CONSTITUTION:Outside the distribution pipe of mixed gas installed at the center of heat exchanger tube 1 with a exhaust nozzle 2 at its end, sec air pipe is installed coaxially with a specified space. On the outside surface of distribution pipe 5, many spouting nozzles 6 of mixed gas are protruded at regular intervals circumferentially and axially. As mixed gas spouted from nozzles 6 is burnt via divergent nozzles 7, the gas expands and the gap between nozzle 6 and divergent nozzle 7 is in negative pressure by its energy, and therefore, sec. air is drawn in and supplied to flame. As a result, high temperature flame is formed and all parts of the heat exchanger tube 1 are uniformly heated up.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a multi-hole burner with heat transfer tubes that transmits heat to the outside via heat transfer tubes.

(Prior art) Electric sheathed heaters have been known as heating means equipped with uniform heating heat transfer tubes, but sheathed heaters have four
The energy conversion rate is only around 0%, and due to insulation problems within the heater, a surface temperature of around 500° C. is considered to be a practical range.

To compensate for this, a burner is installed at the inlet of the tube, such as a radiant tube, which transfers high-temperature heat by forcing direct combustion gas through the heat transfer tube. There is also a type that heats the heat transfer tube by circulating it and transfers the heat to the outside.

(Problem to be solved by the invention) However, in the case of this type of tube, the temperature difference between the inlet of the heat transfer tube where the burner is located and the exhaust port on the opposite side becomes large, and the temperature difference increases over the entire length of the heat transfer tube. It has the disadvantage that it cannot be uniformly heated over a long period of time. Therefore, extreme heating occurs, which affects the object to be heated. In addition, with conventional immersion tube burners that heat foods such as tempura by passing a heat transfer tube horizontally into an oil tank, the flame does not burn well due to the buoyancy of the gas, so only the upper half of the heat transfer tube acts as a heat transfer section. First, the lower half had the disadvantage that it was not very useful for heat transfer. In addition, in the conventional type, the combustion gas (CO2) increases toward the outlet of the heat exchanger tube, and the more it goes toward the outlet, the more
(incompletely combusted gas), which worsens the combustion environment and makes it difficult to form a flame. This is because Bunsen type burners and similar burners use the air (02) in the heat transfer tubes to provide the secondary air necessary for completing combustion. Therefore, it is necessary to make the diameter of the heat exchanger tube larger than necessary so that excess air can be sucked in. As a result, the temperature inside the heat exchanger tube becomes low, and since the amount of radiant heat transfer is determined by TK4, a considerably large heat transfer surface is required. There was a drawback.

An object of the present invention is to provide a multi-hole burner with a heat exchanger tube that can uniformly heat the heat exchanger tube in both the longitudinal direction and the circumferential direction.

(Means for Solving the Problems) The structure of the present invention that achieves the above object will be explained with reference to FIGS. 1 to 3 corresponding to embodiments. The present invention has an exhaust port 2 at the tip. Secondary air distribution inside the heat exchanger tube 1 with! i
4 and a mixed gas distribution pipe 5 are arranged concentrically at a predetermined interval so that the mixed gas distribution pipe 5 is located at the center.

A large number of mixed gas jetting nozzles 6 are protruded from the outer periphery of the mixed gas distribution pipe 5 at predetermined intervals in the circumferential and longitudinal directions.

On the outer periphery of the secondary air distribution pipe 4, flared secondary air suction tubes 7 are protruded in correspondence with the respective nozzles 6 so as to communicate between the inside and the outside.

Each tip of the secondary air distribution pipe 4 and the mixed gas distribution pipe 5 is closed. A secondary air suction venturi pipe 9 is connected to the base end of the secondary air distribution pipe 4. At the base end of the mixed gas distribution pipe 5, a mixed gas forming suction venturi pipe 11 is connected to the secondary air suction venturi pipe 9.
They are arranged concentrically with each other. A fuel gas injection nozzle 12 and a primary air intake part 13 are provided at the inlet of the venturi pipe 11 for forming and suctioning the mixed gas. Said 2
A secondary air intake section 16 is provided at the entrance of the venturi tube 9 for secondary air intake.

(Function) If the mixed gas jetting nozzle 6 is provided protrudingly in the mixed gas distribution pipe 5 in this way, and the secondary air suction tube 7 is correspondingly provided in the secondary air distribution pipe 4, the air is jetted from the nozzle 6. The mixed gas burns in the flared cylinder 7, resulting in about 6 to 8
It is expanded twice, and the energy creates a negative pressure in the gap between the nozzle 6 and the tube 7 that widens toward the end, and secondary air is sucked in and supplied to the flame, forming a hot flame. Since such an action is performed in the same way at the tip of each nozzle 6, each part of the heat exchanger tube 1 is uniformly heated.

(Example) Examples of the present invention will be described in detail below with reference to FIGS. 1 to 3. As shown in the figure, the multi-hole burner with heat transfer tubes of this embodiment has heat transfer tubes of round, square, polygonal, etc.
R1, and an exhaust port 2 is provided at the tip thereof.

The heat exchanger tube 1 is provided with a radial residual heat recovery section 3 in front of the exhaust port 2.

Inside the heat exchanger tube 1, there are a secondary air distribution pipe 4 and a mixed gas distribution pipe 5.
Toga Z mixed gas distribution! 25 is located in the center, and are arranged concentrically at a predetermined interval. A large number of tapered mixed gas ejection nozzles 6 are protruded from the outer periphery of the mixed gas distribution pipe 5 at predetermined intervals in the circumferential and longitudinal directions. On the outer periphery of the secondary air distribution pipe 4, a secondary air suction tube 7 is protruded in correspondence with each nozzle 6 so as to communicate between the inside and the outside. Fire transfer holes 8 are provided in the middle of these secondary air suction tubes 7 that expand toward the end. The ends of the secondary air distribution pipe 4 and the mixed gas distribution pipe 5 are closed. A secondary air suction venturi tube 9 is connected to the base end of the secondary air distribution pipe 4, and the base end of the tube 9 is led out through the end plate 10 at the base end of the heat transfer tube 1. There is. At the base end of the mixed gas distribution pipe 5, there is a venturi pipe 11 for forming and suctioning a mixed gas, and a venturi pipe 9 for suctioning secondary air.
The heat exchanger tube 1 is connected concentrically to the heat exchanger tube 1, and is similarly led out to the outside of the heat exchanger tube 1. Venturi tube 11 for mixed gas formation and suction
A fuel gas injection nozzle 12 is provided at the center of the inlet, and a primary air intake portion 13 is provided at the outer periphery of the fuel gas injection nozzle 12. The primary air intake section 13 is provided with a primary air damper fixing section 14 and a primary air damper rotating section 15 . A secondary air intake section 16 is provided at the entrance of the venturi tube 9 for secondary air intake. The secondary air intake section 16 is provided with a secondary air damper fixing section 17 and a secondary air damper rotating section 18 . The fuel gas injection nozzle 12 is provided with a gas flow rate adjustment section 19, and is connected to a fuel supply pipe 20. The primary and secondary air damper rotation parts 15.18 and the gas flow rate adjustment part 19 are interlocked and adjusted by an air-fuel ratio adjustment link mechanism 21.

In such a multi-hole burner, the nozzle 12
The fuel gas ejected from the primary air intake section 13 is mixed with the primary air taken in from the primary air intake section 13 in the mixed gas forming suction venturi pipe 11, and is sucked in as a mixed gas. The secondary air is distributed from each nozzle 6 into the secondary air suction tube 7 .

In this state, when one to several secondary air suction flared tubes 7 are ignited, all the remaining secondary air suction tubes 7 are ignited through the spark transfer holes 8. The combustion of the mixed gas in these diverging cylinders 7 heats the wall of said 117, and a primary flame 22 is formed in the direction of the nozzle 6. Nozzles 6 and 2
Next air intake spreads I! When used in combination with 7,
When the mixed gas ejected from the nozzle 6 is combusted, the gas spreads out to about 6 to 8 times and expands at the tip of the tube 7.
The energy creates a negative pressure in the gap between the nozzle 6 and the tube 7 that widens toward the end, and secondary air is sucked in and supplied to the primary flame 22, forming a high-temperature secondary flame 23. Since the ejecting of the mixed gas and the supply of secondary air are performed in each of the tubes 7 that widen toward the end, each part of the heat exchanger tube 1 can be uniformly heated. The flared cylinder 7 is heat-retained by the flames 22 and 23 and is appropriately cooled by the secondary air, thus serving as a flame insulator.

Note that the secondary air is supplied at a ratio of 20 to 60 parts per 100 parts of the primary air.

(Effects of the Invention) As explained above, in the multi-hole burner with heat transfer tubes of the present invention, the secondary air distribution pipe and the mixed gas distribution pipe are arranged concentrically within the heat transfer tube, and the outer periphery of the central mixed gas distribution pipe is Since a large number of mixed gas ejection nozzles are protruded at predetermined intervals in the circumferential direction and longitudinal direction, the mixed gas can be ejected almost uniformly from each position in the circumferential direction and longitudinal direction of the mixed gas distribution pipe.

In addition, in correspondence with these nozzles, secondary air suction tubes protruding from the outer periphery of the secondary air distribution pipe are provided so as to communicate between the inside and outside, so that the mixed gas ejected from each nozzle is transferred to the corresponding flared tube. The energy expands greatly when it burns inside the flame, and the energy creates a negative pressure in the gap between the re-nozzle and the flared cylinder, allowing the secondary air to be effectively sucked in and supplied to the primary flame, increasing the temperature of each flame. You can obtain a secondary flame of. Therefore, according to the present invention, even if the heat exchanger tube is used horizontally, almost uniform combustion can be obtained even in the lower portion, and uniform heating of the heat exchanger tube can be achieved.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view of an embodiment of the burner according to the present invention, FIG. 2 is a cross-sectional view taken along ■--■ in FIG. 1, and FIG.
It is a 1-line sectional view. 1... Heat exchanger tube, 2... Exhaust port, 4...
...Secondary air distribution pipe, 5...Mixed gas distribution pipe, 6...Mixed gas injection nozzle, 7...
・Secondary air suction tube expanding at the end, 8... fire transfer hole,
9... Venturi tube for secondary air suction, 11.
...Venturi tube for forming and suctioning mixed gas, 12.
... Fuel gas injection nozzle, 13 ... Primary air intake section, 16 ... Secondary air intake section. Ipgo) Management

Claims (1)

[Claims] A secondary air distribution pipe and a mixed gas distribution pipe are arranged concentrically at a predetermined distance apart from each other at a predetermined interval, with the mixed gas distribution pipe located in the center, in a heat transfer tube having an exhaust port at the tip,
A large number of mixed gas jetting nozzles are protruded from the outer periphery of the mixed gas distribution pipe at predetermined intervals in the circumferential and longitudinal directions, and secondary air is ejected from the outer periphery of the secondary air distribution pipe corresponding to each nozzle. A suction tube that expands at the end is protruded so as to communicate between the inside and the outside, each tip of the secondary air distribution pipe and the mixed gas distribution pipe is closed, and a secondary air suction tube is provided at the base end of the secondary air distribution pipe. A Venturi tube for suction for forming a mixed gas is connected to the base end of the mixed gas distribution pipe, and a Venturi tube for suction for forming a mixed gas is connected concentrically to the Venturi tube for suctioning the secondary air. A fuel gas injection nozzle and a primary air intake section are provided at the inlet of the Venturi tube, and a two
A multi-hole burner with a heat transfer tube, characterized by being provided with a secondary air intake section.