JPS58117913A - Combustor - Google Patents

Abstract

PURPOSE:To obtain a combustor capable of preventing the increase of pressure loss in air passage even when primary air and gas are synchronously supplied in terms of amount and TDR is greatly taken. CONSTITUTION:Since a primary air passage 11, a secondary air passage 12, and a gas pathway 14 are controlled so that they are kept at a fixed area ratio, both the primary air and secondary air are controlled with respect to air-fuel ratios. Also, since the pressure of a high-pressure portion 18 is fedback to the pressure chamber 19 of a pressure-equalizing valve 13 in such a way that the pressure difference between the high-pressure portion 18 and low-pressure portion 21 of the primary air passage 11 is equalized with the pressure difference between the gas outlet of the valve 13 and the connection between the gas pathway 14 and the low-pressure portion 21, the air-fuel ratio on the primary air side can be kept almost constantly with good accuracy by the pressure- equalizing valve. Thus, a wide range of stable combustion can be obtained and also high-load combustion can be attained.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a combustion device that performs high-load stable combustion by supplying secondary air to a premixed flame, and particularly relates to a combustion device that requires air-fuel ratio control and combustion amount control. .

Conventionally, combustion methods for performing high-load combustion include all-fire combustion, forced Bunsen combustion that supplies secondary air to a premixed flame, and the like. The former is a combustion that premixes all the air required for combustion, and the air-fuel proportional means is a so-called air-fuel proportional means that supplies a gas h1° according to the difference 1!: of the mixing pipe section installed in the supply air path. A one-way zero governor system has been considered. According to this system, when combustion I11: 'nJ change is required, the differential pressure in the mixing tube is proportional to the square of the combustion h111 change width, and for example, when the minimum combustion If the differential pressure is 8mmq, multiplying the combustion amount by 6 will result in a differential pressure of 200M1kq, and the pressure loss is proportional to the differential pressure, so T, D, and R should be set large. However, there were practical problems in using it for household equipment, as it required setting the blower's air pressure to a very high level, making the blower large, and producing high air noise.

Further, in all-flame combustion, since more than the stoichiometric amount of air is premixed, backfires are likely to occur and the combustion range is narrow.

In forced Bunsen combustion, the t-mixture is set at, for example, 30% to 60% of the theoretical air, and the system completes combustion by supplying secondary air, so compared to the full-primary combustion mentioned above. And don't start a punk fire, 'J:D.
It has the characteristic of being able to obtain a large R, but in order to do so, it is necessary to control the primary air side and secondary air side J in accordance with the combustion 111, and since there is no good means for doing so, it is not possible to use household combustion equipment. In this case, it was common to control the combustion area by -1.

The combustion device of the present invention employs a forced Punze/combustion method that uses primary air,
It aims to control the air-fuel ratio of both the secondary air and, in particular, synchronizes the primary air amount and gas supply amount, and is a combustion method that can prevent an increase in pressure loss in the air passage even when T, D, and R6 are large. The purpose is to provide a device.

The present invention provides combustion by supplying secondary air perpendicularly or at a certain angle to the flame port for spouting the premixture and the jetting direction of the premixture, and the secondary air supply position is located at the premixture flame. high-load combustion is achieved.

In order to achieve the above-mentioned high-load combustion, it is necessary to maintain a substantially constant air-fuel ratio for both the premixture and the secondary air. The passageway R1 is led from the equalizing pressure plate 1, and each passage of the block is provided with a differential pressure generation part, and the passage area of the differential pressure generation part is made to have approximately the same ratio for each passage. Since it has phase control stage 1, which narrows down the fuel gas amount and primary air Mht.
, secondary air 111 are controlled at approximately the same ratio. 1 more
The pressure in the high pressure part of the differential pressure generating part of the secondary air passage is fed back to the pressure chamber of pressure equalizing valve 1, and the differential pressure generating part of the gas passage is communicated with the low pressure side of the differential pressure generating part of the primary air passage. Therefore, the differential pressure of the primary air differential pressure generating section and the gas supply pressure become the same, and the primary air and fuel are supplied at a constant set ratio.

Now, as a means to change combustion 111 to uJ,
By varying the area of each passage using means, the air-fuel ratio is maintained at a constant level on both the primary air side and the secondary air side.In particular, on the primary air side, an equalizing valve is used to adjust the pressure of gas and air. Since the air-fuel ratio is synchronized, the air-fuel ratio becomes a constant set value with good viscosity.

Hereinafter, one embodiment of the present invention will be explained based on the drawings. Figure 7 shows a configuration principle diagram showing an embodiment of the present invention in a water heater. In the figure, 1 is the burner and air mixture chamber 2. Slit-shaped flame mouth 3. Secondary air chambers provided on the left and right4. There is a secondary air supply port 6 for supplying secondary air perpendicular to the air-fuel mixture jetting direction, 6 is a combustion chamber, 7 is an endothermic fin, and 8 is an endothermic pipe. A block 9 is divided into a primary air passage 11 and a secondary air passage 12 connected to the blower 1o.
It communicates with the gas passage 14 of the block 9 via a pressure equalizing valve 13. Each passage 11.12.1 of block 9
4 is provided with a bench-like differential pressure generation section, and a control mechanism 1 that controls the area of each passage by connecting and sliding a needle 16 that narrows down the population area ratio of each pencilly at a constant ratio.
6 is provided, and 17 is the control 41! This is a drive unit that slides the structure 16.

The pressure in the high pressure section 18 of the primary air passage 11 is fed back to the pressure chamber 19 of the pressure equalizing valve 13 through a connecting pipe 20, and the gas passage 1 is fed back to the low pressure section 21 of the primary air passage 11.
4 are connected and communicated with the mixture chamber 2 through the mixture passage 22.

On the other hand, the secondary air passage 12 is communicated with the secondary air chamber 4 through a secondary air supply pipe 23.

In the above configuration, the primary air passage 11, secondary air passage (passage 12, and gas passage 14) are controlled to have a constant area ratio. control is carried out, and - the next air passage 11
The differential pressure between the high pressure part 18 and the low pressure part 21 of the pressure equalizing valve 13 and the barrier of the gas outlet part of the gas path 14 and the connection part to the low pressure part 21 are
- Since the pressure of the high IT section 18 is fed back to the pressure chamber 19 of the pressure equalizing valve 13 so that the pressure is
The air-fuel ratio on the secondary air side is precisely controlled to a substantially constant ratio.

High-load combustion is achieved by setting the air-fuel ratio of the primary air with high precision and supplying the secondary air with approximately controlled air-fuel ratio to the premix flame, making it possible to burn a wide range of combustion.

Furthermore, the primary air passage 11° and the secondary air passage 12. The primary control means controls the area of each passage portion of the gas passage 14 to keep the area ratio constant.

Since the amount of secondary air and gas can be controlled at a nearly constant ratio, the amount of combustion can be controlled by the control means, and it is also possible to detect the hot water coming out and perform so-called proportional control to reach the set hot water temperature. It is possible.

When performing this proportional control, the blower 1o is operated with a constant applied voltage, and when reducing the amount of combustion, the needle valve 16 is used to throttle the openings of the respective passages 11, 12, and 14. high pressure section 18 of the primary air passage 11 when The differential pressure between the low-pressure parts 21 only needs to be the minimum differential pressure necessary to obtain a constant air-fuel ratio with high accuracy by the pressure equalizing valve 13. If the combustion amount is reduced, the area is reduced, so the differential pressure increases, but the blower Since it is sufficient to operate under the same conditions as when the combustion amount is large, the combustion amount can be varied over a wide range without increasing the capacity of the blower.

As is clear from the above embodiments, the following effects can be obtained according to the present invention.

(1) Each passage section is controlled with the same area ratio, so the primary air
The air-fuel ratio of both the secondary air can be controlled, and the air-fuel ratio of the primary air can be kept almost constant with high precision using a pressure equalization valve, allowing stable combustion over a wide range and achieving high-load combustion. Ru.

(2) By controlling the areas of the primary air passage, secondary air passage, and gas passage at a nearly constant ratio, it is possible to control the combustion 111° as well as the air-fuel ratio, and perform so-called proportional control on the gas 1d and the control valve. This can be achieved without using etc.

(3) When performing the above-mentioned combustion 111° control, by setting the primary air passage differential pressure to the necessary minimum pressure at the maximum combustion 1.1, the air-fuel ratio on the primary air side is controlled to 0 (pressure equalized) Since the combustion rate is controlled by 1, there is no need to increase the blowing capacity even if the combustion amount is controlled, which eliminates the disadvantages of conventional methods such as the blower becoming larger and the blowing noise being higher. °J, can be solved.

[Brief explanation of drawings]

The figure is a configuration diagram of a dead tree that is motivated by supply, which is an embodiment of the present invention. Machine, 11...Primary air passage, 12...
Secondary air passage, 13... pressure equalization valve, 14...
...Gas path, 18...High pressure section, 19...
・Pressure chamber, 21...Low pressure section. Name of agent: Patent attorney Toshio Nakao and one other person ρ7

Claims (1)

[Claims] The block includes a burner that supplies secondary air to a premixed flame, and a block that is provided with a primary air passage communicating with a blower, a secondary air passage, and a gas passage communicating with a pressure equalization valve, and has a differential pressure in each passage of the block. a means for controlling the area of the differential pressure generating section to be approximately the same in each passage; A combustion apparatus having a structure in which a gas passage on the downstream side that feeds into the chamber and controls the area is communicated with a low pressure part of the primary air passage, and the combustion amount is controlled by the control means.