JPS58193039A - Heater - Google Patents

Abstract

PURPOSE:To miniaturize the heater as a whole by arranging a heat exchanger adjacent to the flame forming surface of a burner. CONSTITUTION:The total primary air burner 2 is constituted substantially to a plate shape by a heat-resistant material such as ceramics, and a plurality of burner ports 10 facing to a gas chamber 7 are formed. A mixed gas of fuel gas and air for combustion supplied to the gas chamber 7 passes through the burner ports 10, and short flames are formed to the flame forming surface 11 on the side reverse to the gas chamber 7. The heat exchanger 1 is set up adjacent to the flame forming surface 11 of the total primary air type burner 2. The heat exchanger 1 is formed by fastening a plurality of fins 13 to the outer circumferential surface of a heat transfer pipe 12 extending in parallel with the flame forming surface 11 at intervals in the axial direction. Sections among each fin 13 in the heat exchanger 1 are filled with a granular substance 17 in an extent that the flow of combustion exhaust gas is allowed while being supported by a support gauze 16. The granular substance 17 is formed by a heat-resistant material, such as alumina, silica and other ceramics, etc.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a heating device, and more particularly, to a heat exchanger configured by fixing fins to the outer peripheral surface of a heat transfer tube through which a fluid to be heated flows. The present invention relates to a heating device for heating the fluid to be heated.

Such heating devices have conventionally been used, for example, gas heating devices. l
This is realized using t+ equipment. However, in the past, in order to secure a combustion space for complete combustion, the distance between the burner and the heat exchanger was chosen to be relatively large, resulting in an increase in the size of the entire heating device. In order to eliminate such drawbacks, it is simply conceivable to shorten the distance between the burner and the heat exchanger by using an all-air burner that can obtain a short flame. However, since the wall surface of the heat exchanger is at a low temperature, if the distance is shortened, the combustion of the fuel gas will not be completed near the flame formation surface of the all-air burner, and will be cooled by the heat exchanger. Carbon monoxide is generated due to incomplete combustion. To prevent this, the HiU short distance must be made large, and as a result, the combustion chamber must be made large. Furthermore, if the total fuel ratio of the all-primary air type parner is made small in order to shorten the flame length, the combustion temperature becomes large. As a result, the total air burner itself may become overripe and burn out, or
The amount of No. generated becomes large. Furthermore, backfire phenomenon tends to occur, which is dangerous.

An object of the present invention is to solve the above-mentioned technical problems and to provide a heating device whose combustion chamber is made smaller so that the overall size of the heating device can be reduced.

Hereinafter, the present invention will be explained in detail with reference to the drawings.

FIG. 1 is a tangled vertical I#rOI of an embodiment of the present invention]
It is a diagram. A fluid to be heated, such as water Vi, is supplied to a heat exchanger 1 as shown by a solid line arrow 3, and is heated in this heat exchanger 1 by exchanging heat with the combustion exhaust gas from the all-air parlor 2. The wet water after heating is drawn out as shown by arrow 4,
Used for hot water supply, hot water heating, etc.

The gauging 6 of this heating device i15 is configured, for example, in the shape of a mountain with an open bottom. Inside this gauging 6, a total air burner 2 (2) is provided on a fixed surface with its peripheral edge in close contact with the inner surface of the casing 60, and the gas chamber is formed by this total air burner 2 and the inward direction of the gauging 6. 7 is specified. A gas supply pipe 8 is connected to the gauging 6 to communicate with the gas chamber 7, and from this gas supply pipe 8, as shown by the arrow 9, a mixture of the soybean gas and the baking air is supplied. Power gas is supplied to the gas chamber 7.

Referring to FIG. 42, a total air burner 21'i is made of a heat-resistant material, such as ceramic, and is substantially plate-shaped, and has a plurality of flame holes 10 formed in the gas chamber 7. The mixed gas of fuel gas and combustion air supplied to the gas chamber 7 flows through the flame hole 10 and forms a short flame in a flame cone 11 on the opposite side from the gas chamber 7.

Heat exchanger IVi, flame forming surface 1 of total confinement type Pana 2
1. This heat exchanger l has an axial force (
(b) It is made by fixing the return fins 13 at intervals of K.

A heated fluid supply pipe 14 for supplying heated fluid is connected to one shoulder of the transmission pipe 12, and a heated fluid outlet for discharging the heated fluid after heating is connected to the other end. Pipe 15 is connected.

A support @ 16 is provided below near the heat exchanger 1, with its peripheral edge supported by the inner surface of the gauging 6.

In the heat exchanger I, between each fin 13, supported by the support wire mesh 16, particulate matter 17 is filled to the extent that the flow of the combustion exhaust gas is fF. This particulate matter 1
7 is formed from a heat resistant material such as alumina, silica and its like ceramics.

In order to heat the fluid to be added with such a heating device (115), a mixed gas of fuel gas and combustion air is supplied to the gas chamber 7 at a temperature of, for example, 1.4°C.
- The next pneumatic PANA 2 will be manned. As a result, a short flame is formed in the flame formation Ii[ill, and the flue gases are discharged through the granules 17 of the heat exchanger 1. The particulate matter 17 is heated by contact with the combustion exhaust gas and becomes red-hot, and its radiant radiation promotes heat transfer to the fins 13.

Furthermore, by flowing through the particulate matter 17, the flow of the combustion υ1 gas inevitably becomes turbulent, which lowers the heat transfer coefficient to the fins 13 and heat transfer tubes 12. Heat transfer to the heated fluid in the exchanger 1 is promoted, and the heat transfer area of the heat exchanger 1 can be reduced.

Further, since the particulate matter 17 becomes reddish-like, the combustion of unburned substances in the combustion exhaust gas is promoted by the catalytic effect. Therefore, generalized Rx is prevented from being included in the combustion exhaust gas discharged from the bottom m of the casing 6. Therefore, even if the heat exchanger 1 is placed close to the flame formation direction 11,
No unburned gas is generated, and the enclosure can be constructed compactly. Furthermore, since the fuel gas is combusted in a small combustion chamber, high-load combustion is possible, and there is no need to unnecessarily reduce the air-fuel ratio and combust at high temperatures, so the amount of NO generated is can also be kept low.

Note that even if the particulate matter 17 is burnt out, it hardly affects the burning performance.

FIG. 3 is a simplified W8 Mwr curve diagram of another embodiment of the present invention, and parts corresponding to the embodiments of FIGS. 1 and 2 are given the same reference numbers. In this embodiment, a heat exchanger 23 is provided in which heat exchanger tubes 20, 21, and 22 are arranged in mantissa, for example, three rows, at intervals along the flow direction of the combustion exhaust gas, and the heat exchanger tubes 20 are all It is arranged close to the flame formation direction 11 of the secondary pneumatic parner 2. The outer periphery of the heat exchanger tube 20 is provided with a relatively large interval (for example, 5 to 5 mm) in the axial direction.
A plurality of fins 24 having a large wall thickness and a small protrusion are fixed at intervals of 7 mm), and particulate matter 17 is filled between each fin 24. A plurality of fins 25° 26 with a small wall thickness are fixed to the outer periphery of the heat exchanger tubes 21 and 22 on the downstream side of the heat exchanger tube 20 at relatively small intervals (for example, 2 to 3 mm) in the axial direction. be done. Further, the amount of radial outward protrusion of each fin 25.degree. 26 is selected to be large.

According to this embodiment, the fin area of the fins 24 close to the flame formation direction 11 is small and the wall thickness is large;
Burnout of the fins 24 is prevented.

In addition, the lack of heat transfer area in the heat transfer tube 20 is caused by heat transfer '1J.
This is compensated for by the large fin area of 21.22. Note that even if the thickness of the fins 25 and 26 is small, there is no risk of burnout because the combustion exhaust gas is reduced by 1M degrees in the heat exchanger tubes 21 and 22.

In the embodiment described above, the air exchanger 1.23 is placed below the air burner 2, but in another embodiment of the present invention, the air exchanger 1.23 is placed above the air burner 2. 1.23 may be placed. However, when the heat exchanger 1.23 is placed below the total air burner 2, the moisture in the vertically assembled combustion exhaust gas is cooled by the heat exchanger 1.23. This is convenient because the air does not drop onto the burner 2.

As described above, according to the present invention, the heat exchanger can be disposed close to the direction of flame formation of the firefly confinement type parner, so the overall size can be reduced.

4. The 6th brother responsible for drawings (7) Figure 1 is a simplified vertical cross-sectional view of an embodiment of the present invention, Figure 2
The figure is a perspective view of the total air burner 2, and the third figure is a vertical to rnto view of another embodiment of the present invention.

1.23... Heat exchanger, 2... Total air type parna, 5
... Heating device, 6. Gushing, 7. Gas chamber,
10...flame hole, 11...flame formation direction, 12,20,
21.

22...transmission tube, 13.24, 25.26-...fin,
17... Particulate matter agent Patent attorney Kei Shikyo - Immediately 1st I! ! ! 1 Figure 2 Figure 3

Claims (3)

[Claims] (1) The s! is constructed by fixing fins to the outer peripheral surface of a heat transfer tube through which the fluid to be heated flows through which the combustion exhaust gas from the burner flows. In the heating device which heats the fluid to be heated in the exchanger, the casing contains fuel gas and combustion fluid. A gas chamber to which air is supplied is formed, and a substantially flat all-air burner made of a heat-resistant material and having a plurality of flame holes extending Km into the gas chamber is provided; A heat transfer tube of the heat exchanger is arranged close to the flame forming surface of the heat exchanger, and particulate matter made of a heat-resistant material is filled between the heat transfer fins to allow the flow of combustion exhaust gas. heating device. (2) The heat exchanger is arranged in multiple rows at intervals of 'lk along the flow direction of the combustion exhaust gas from the all-air burner, and the fins of the heat exchanger tubes are located at the position closest to the all-air burner. The fins are provided with relatively large intervals between each other, and curved particulate matter is filled between each fin, and the heat transfer tube on the downstream side in the flow direction is provided with fins with relatively small intervals between each fin. The heating device according to claim 1, characterized in that: (3) The fins of the heat exchanger tube at the position closest to the total air type parner are provided with a large wall thickness and a small protrusion, and the fins of the heat exchanger tube on the downstream side in the flow direction are provided with a thick wall. The heating device according to claim 2, characterized in that it is provided with a small thickness and a large protruding mold.