JPH031009A - gas burner equipment - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an all-primary mixing type gas burner device.

[Conventional technology]

When using a gas burner such as a water heater that proportionally controls the combustion load using the all-primary mixing method, the quality of air ratio control becomes a problem because the combustion range is much narrower than that of the Bunsen method.

For this reason, conventionally, an electronic control method has been adopted in which the combustion state is detected by a sensor and fed back, and the gas amount and air amount are individually controlled.

On the other hand, conventionally, as shown in FIG. 7, the ratio control valve section C is configured so that three diaphragms 11° 12.13 and a valve body 14 are interlocked (in the vertical direction). There is a gas burner device that controls the secondary pressure of raw gas supplied to the gas burner section G by sensing the fan pressure of combustion air in the gas burner G using a diaphragm 11.

[Problem to be solved by the invention]

However, in the former case, (1) electronic control is used, which complicates element conversion and the number of parts in the feedback circuit, and increases the number of parts.As a result, maintenance is time-consuming and reliability is poor; Moreover, it has the disadvantage that production costs are high.

(2) In order to minimize changes in the amount of air due to gusts of wind, etc., it is necessary to increase the source pressure of the combustion air, so it is necessary to increase the rotation speed of the blower fan or increase the fan diameter. For this reason, the production cost of the blower fan becomes high, and furthermore, there are disadvantages in that noise and the like are likely to be generated.

On the other hand, in the latter case, in the ratio control valve section C, the weight of the movable part and the repulsive force of the spring 15 are taken into consideration in addition to the air pressure as counterforces to be balanced against the secondary pressure of the raw gas. This method had the disadvantage of having to constantly control the air ratio to the amount of raw gas.

Moreover, when a gust of wind is applied to the exhaust port of the gas burner, the internal pressure in the air chamber increases even though the air flow rate decreases, so the ratio control valve section C operates in the direction of opening the valve 14. However, as a result of changing the air ratio, in a burner with a narrow combustion range such as an all-primary mixer burner, there is a disadvantage that it is difficult to control the air-fuel ratio with high precision while receiving disturbances such as gusts of wind.

The object of this invention is to eliminate these disadvantages.

[Means to solve the problem]

In order to achieve the above object, the gas burner device of the present invention includes a gas burner section, a blowing means, and a ratio control valve section, and supplies raw gas to the gas burner section through the ratio control valve section and the nozzle. In the forced combustion gas burner device which supplies combustion air by the blowing means, in configuring the ratio control valve section, a first diaphragm, a second diaphragm are arranged in a substantially cylindrical body along its axis in order from one end. By arranging the diaphragm, the third diaphragm, and the valve body and fixing an operating rod at the center of each of the diaphragms and the valve body, these diaphragms and the valve body can be interlocked, and the first diaphragm and the cylinder A first chamber exists between the bottom plate at one end of the body, a second chamber exists between the first diaphragm and the second diaphragm, a third chamber exists between the second diaphragm and the third diaphragm, and a third chamber exists between the second diaphragm and the third diaphragm. A fourth chamber is provided between the diaphragm and the valve body, a fifth chamber is provided between the plate valve and the bottom plate at the other end of the cylinder, and a gas inlet and a gas outlet are provided in the cylinder, and the gas The raw gas can be introduced into the fourth chamber through the inlet, and the raw gas from the fifth chamber can be supplied to the gas burner section through the gas outlet, and the first chamber and the exit side of the nozzle The fifth chamber and the inlet side of the nozzle are communicated with each other via a gas supply pipe, and the second chamber and the burner inlet side are communicated with each other via a second communication passage. The third chamber and the outlet side of the burner section are communicated through a third communication passage, and the pressure receiving areas of the first diaphragm, the third diaphragm, and the valve body are approximately equal. and the pressure receiving area of the second diaphragm is larger than the pressure receiving area of the first diaphragm, the third diaphragm, and the valve body, and further, the second communicating passage and the third communicating passage are communicated by a bypass passage. A pressure loss means is installed in either one of the second communication passage, the third communication passage and the bypass passage, and the pressures thereof can be adjusted by at least one of the long means.

Note that a compression spring may be interposed between the operating rod and the bottom plate at the other end of the cylinder, and the spring force of this compression spring may be adjustable.

[Action of the invention]

Since the gas burner device according to this explanation is configured as described above, the nozzle outlet pressure P can be detected in the first chamber 71 of the ratio control valve section, and the nozzle population pressure P2 can be detected in the fifth chamber. , Differential pressure between burner section inlet pressure P3 and burner section outlet pressure P4 (p
s P4) partial pressure (p,'-p,) can be detected in the second and third chambers. Additionally, the supply gas pressure can be detected in the fourth chamber.

Therefore, when the amount of air blown (combustion air) is increased, the partial pressure (Ps' P
4) As a result, the second diaphragm (air differential pressure receiving part) 62 is pushed downward (in the figure), and as a result, the plate valve 92 is displaced in the opening direction via the operating rod 8, and the air flows to the burner part G. The amount of raw gas increases. Then, the differential pressure p, -Ps on both sides of the nozzle ("nozzle outlet side and nozzle inlet side", the same applies hereinafter) increases, and the first diaphragm 61 and the plate valve (raw gas differential pressure receiving part) 92 receive pressure and operate. The load on the rod 8 in the closing direction of the plate valve 92 increases, and these two differential pressures (p, -Pa and Pt Ps) apply loads in opposite directions via the operating rod 8, so that the operating rod 8 is displaced until these loads are balanced, and converges to a position where the opposing forces of the burner section both-side differential pressure receiving section 62 and the nozzle both-side differential pressure receiving section 61.92 are balanced, and the amount of raw gas is supplied.

At this time, the air ratio is determined only by the physical property constants of gas, air, etc., the fluid constants of the passages, the area ratios of the respective pressure receiving parts, etc., and this air ratio remains constant even if the amount of air changes.

Further, by adjusting the pressure loss means, the second diaphragm 62
By adjusting the differential pressure applied to the air, the air ratio can be easily adjusted.

Note that if a compression spring is interposed between the operating rod and the bottom plate at the other end of the cylinder, and the spring force of this compression spring is adjustable, the compression spring (between the operating rod and the other end of the cylinder) can be adjusted. It is possible to fine-tune variations in the spring characteristics of the compression spring (between the bottom plate and the bottom plate), and it is also possible to easily adapt the air ratio characteristics to the burner.

[Explanation of Examples]

Embodiments of the present invention will be described below based on the drawings.

In FIGS. 1 to 3, G is a gas burner section of the gas water heater 1, and C is a ratio control valve section.

First, the gas burner section G will be explained.

21 is an air chamber case, 22 is a mixing chamber case installed within the air chamber case 21, and 23 is a heat exchanger inner shell installed above the air chamber gas 21. In this case, the air chamber case 21
The space between the mixing chamber case 22 and the mixing chamber case 22 constitutes an air chamber A, and the inside of the mixing chamber case 22 constitutes a mixing chamber M. Reference numeral 24 denotes a blower fan, which is provided in a protruding manner on the air chamber case 21 . Combustion air is supplied to the air chamber A by this ventilation fan 24. Reference numeral 3 denotes a gas supply pipe, which is arranged on the bottom surface of the air chamber case 21. Raw gas is supplied from the ratio control valve section C to the gas burner section G via this gas supply pipe 3. 31 is a nozzle.

The gas supply pipe 3 is provided in a protruding manner. This nozzle 31 protrudes into the mixing chamber M, and has jet holes 311, 311, . . .
- Inject raw gas into the mixing chamber M through. 41.41
．． . . are through holes formed in the bottom plate of the mixing chamber case 22. Combustion air (combustion air supplied by the blower fan 21) is supplied into the mixing chamber M through the through holes 41, 41, . . . and mixed with the raw gas.

Reference numeral 42 denotes a pressure equalizing plate, which is installed near the top of the nozzle 31. This pressure equalizing plate 42 maintains a mixing space and equalizes the pressure of the mixed gas (a mixture of raw gas and combustion air, hereinafter the same).

Reference numeral 43 denotes a flame hole plate, which is installed at the open end of the mixing chamber case 22. Also, 431,431. . . . are pores, which are formed in the flame hole plate 43.

This pore 431, 431. The mixed gas is ejected into the heat exchanger inner shell 23 through... and is combusted. 44 is a heat exchanger, which is installed above the flame hole plate 43 in the heat exchanger inner shell 23. This heat exchanger 44 consists of water pipes 441 and fins 4.
42,442. . . . and heats the water passing through the water pipe 441 by the combustion heat of the mixed gas.

Next, the ratio control valve section C will be explained.

5 is a cylindrical body, and 51.52 is a bottom plate of this cylindrical body 5. Both ends (upper and lower ends) of the cylindrical body 5 are sealed by the bottom plates 51 and 52. Moreover, 53 is a large diameter part,
It is formed in the cylindrical body 5. This large diameter portion 53 has the same axis as the cylindrical body 5. Reference numeral 8 denotes an operating rod, which is arranged along the axis of the cylindrical body 5. This operating rod 8 can move forward and backward in the axial direction of the cylindrical body 5. Reference numeral 91 denotes an annular valve seat, which is formed on the inner surface of the side wall of the cylindrical body 5.

Further, 92 is a disc-shaped plate valve (corresponding to the "valve body" of the present invention), and a bolt 81 is attached to the tip (lower end) of the operating rod 8.
It's stopped. The valve portion 9 is constituted by the plate valve 92 and the valve seat 9I. 93 is a spring seat, and bolt 8
1 and the plate valve 92. Further, 931 is a compression spring, which is installed between the spring seat 93 and the bottom plate (of the cylindrical body 5) 52. This compression spring 9
Reference numeral 31 is for offsetting the weight of movable parts such as the operating rod 8, plate valve 92, and diaphragms 61, 62, 63, which will be described later. Note that a fifth chamber 75 is formed between the valve portion 9 and the bottom plate 52. 63 is the third diaphragm,
It is fitted into the operating rod 8. This third diaphragm 63 is disposed above the valve portion 9 (in FIG. 1), and forms a fourth chamber 74 between it and the valve portion 9. The second diaphragm 63 has the same pressure receiving area as the plate valve 92. A second diaphragm 62 is fitted into the operating rod 8 via a tubular spacer 83. This second diaphragm 62 is installed in the large diameter portion 53 within the cylindrical body 5. This second diaphragm 62 has a larger pressure receiving area than the third diaphragm 63 and forms a third chamber 73 between it and the third diaphragm 63 . This third chamber 73 is connected to the heat exchanger inner shell 23 by a third communication pipe 731.
(corresponding to the "burner outlet side" of the present invention). Therefore, the internal pressure of the third chamber 73 is lower than that of the heat exchanger inner shell 2.
It is equal to the internal pressure P in 3.

Reference numeral 61 denotes a first diaphragm, which is fitted into the operating rod 8 via a tubular spacer 84. This first diaphragm 61 is arranged above the second diaphragm 62 (in FIG. 1), forms a second chamber 72 between the second diaphragm 62, and the bottom 1 (of the cylinder 5) 51. A first chamber 71 is formed between them. The second chamber 72 is connected by a second communication pipe 721 to the air chamber A (corresponding to the "burner section inlet side" of the present invention) and the fixed throttle section 722 (corresponding to the "pressure drop means" of the present invention) described later. are communicated with each other. Therefore, since the internal pressure of the second chamber 72 is equal to the internal pressure P3 of the air chamber A, the pressure reduced by the fixed throttle part 722 (pressure loss means) is applied.

Further, the first chamber 71 is communicated with the outlet side of the nozzle 31 through a first communication pipe 711. For this reason, the first room 7
1 is equal to the internal pressure P on the exit side of the nozzle 31. Note that the first diaphragm 61 has the same pressure receiving area as the third diaphragm 63.

Reference numeral 741 denotes a gas introduction port, which is installed on the side wall (cylindrical body 5) of the fourth chamber 74. Further, 751 is a gas exhaust port, which is installed on the side wall (cylindrical body 5) of the fifth chamber 75. The raw gas is introduced into the ratio control valve section C1, that is, the fourth chamber 74, through the raw gas introduction lower 41, and after passing through the valve section 9, it enters the fifth chamber 75, and then passes through the discharge lower 51 into the cylindrical body. It is discharged from 5. The raw gas discharged from the cylindrical body 5 flows into the mixing chamber M of the gas burner section G via the gas supply pipe 3.

H is a bypass passage, which connects a high-pressure side communication pipe 721A and a low-pressure side communication pipe 731 to two (plural) fixed throttle parts (corresponding to the "one-member pressure means" of this invention) 722 described later and a variable throttle part described later. (corresponding to the "pressure loss means" of this invention) are connected in series. When gas passes through this bypass path H, a differential pressure is generated in each pressure drop means (722 and V). Reference numeral 722 denotes a fixed constriction section, which is installed in the second communication pipe 721. Further, ``■'' is a variable throttle section, which is installed in the bypass path H. By adjusting the pressure loss resistance of the variable throttle section (V), the differential pressure between the second diaphragm 62 and the fixed throttle section 722 and the variable throttle section V
The air ratio can be adjusted by varying the pressure drop resistance of the variable throttle section (2).

Moreover, the fixed throttle part can also be installed in the third communication pipe 731 (see reference numeral 732 in the imaginary line diagram). In this case, the differential pressure between the second communication pipe 721 and the third communication pipe 731 is divided by the pressure drop ratio between the fixed throttle part 732 and the variable throttle part V, and is introduced into the third chamber 73. In addition, a fixed throttle part is installed in the bypass path I (the second communication pipe 721 or the third communication pipe 7
It is also possible to install a variable aperture section in either one or both of 31. The fixed throttle parts 722, 732 and the variable throttle part V constitute the "pressure loss means" of the present invention.

Therefore, this gas burner device operates as follows.

When the amount of combustion air increases, the differential pressure on both sides of the burner (P3
P4) and (P3' P4) become large, pushing the second diaphragm 62 downward (in the figure), and as a result, the plate valve 92 is displaced in the opening direction via the operating rod 8,
The amount of raw gas flowing to the burner section G increases. Then,
The differential pressure P2-P on both sides of the nozzle (“nozzle outlet side and nozzle inlet side”, the same applies hereinafter) increases, and the first diaphragm 61
and the plate valve (raw gas differential pressure receiving part) 92 receives pressure, and the load on the operating rod 8 in the closing direction of the plate valve 92 increases, and these two
Since the two differential pressures (P3'-P4) and (Pz P, ) apply loads in opposing directions via the operating rod 8, the operating rod 8 is displaced until these loads are balanced, and the differential pressure on both sides of the burner section is increased. Pressure receiving part 62 and nozzle side differential pressure receiving parts 61, 92
The opposing forces of the two converge to a balanced position, and the amount of raw gas is supplied.

At this time, the air ratio is determined only by the physical property constants of gas, air, etc., the fluid constants of the passages, the area ratios of the respective pressure receiving parts, etc., and this air ratio remains constant even if the amount of air changes. This will be explained in the examples above. in this case,
S is the pressure receiving area of the first diaphragm 61, third diaphragm 63, and valve body 92, C is the pressure receiving area ratio (large diaphragm area/small diaphragm area) (C>1), and the load direction on the diaphragm and plate valve is −F direction is positive.

(1), Load applied to the gas-related first diaphragm - P, S ... ■ Load applied to the third diaphragm P, S ... ■ Load applied to the plate valve p! S-P, S ... ■ ■1010 is (P, -PS) S ... ■(2)
, Load applied to the first air-related diaphragm Ps'S ... ■ Load applied to the second diaphragm p, cs-p, 'cs ... ■ Load applied to the third diaphragm P4S ... ■ ■+■■ (P, -P,') (C-1)S... ■The difference in load between the above ■ and the above ■ becomes the valve opening/closing force, and the valve portion is displaced until they are balanced. Therefore, in the equilibrium state, ■-〇, (Pg PS)/(P4 Py') =
CI, and the ratio of the gas differential pressure to the air differential pressure is a constant C-1
As a result, even if the air amount is changed, the raw gas amount changes while the air ratio remains constant.

Further, in the present invention, the gas differential pressure is changed by varying one pressure drop resistance. In other words, it has a structure that allows the air ratio to be easily adjusted, so it has wide adaptability (versatility) to various gas fuels and various burners.

FIG. 4 shows the first communication pipe 711 opened to the atmosphere. In the gas burner section G, when the nozzle outlet pressure is negligibly small compared to the nozzle inlet pressure due to the burner structure, the first communication pipe 711 can be opened to the atmosphere in this way, and as a result,
The configuration can be simplified.

FIG. 5 shows a third embodiment, in which the device of the present invention is applied to a fan mixing type gas burner.

FIG. 6 shows a fourth embodiment. In this embodiment, 55 is an adjustment bolt screwed into the bottom plate 51 of the cylinder 5, 551 is a spring seat installed at the tip of this bolt 55, and 552 is between this spring seat 551 and the upper end of the operating rod 8 (in the figure). ) is a passed compression spring. By screwing the adjustment port 55, the compression spring 5
The reason why 52 is adjustable is (2) to enable fine adjustment for variations in the spring characteristics of the compression spring (for offsetting the weight of the moving part) 931 (2).

This is to match the air ratio characteristics to the burner.

In the above-mentioned embodiment, the operating rod 8 is constructed using a - length rod, but the operating rod may also be constructed by bringing the end faces of a plurality of rods into contact with each other to form a - length rod shape.

〔Effect of the invention〕

The gas burner device of the present invention includes a gas burner section, a blowing means, and a ratio control valve section, and supplies raw gas to the gas burner section through the ratio control valve section and a nozzle, and also supplies combustion air by the blowing means. In the forced combustion gas burner device, in constructing the ratio control valve section, a first diaphragm, a second diaphragm, a third diaphragm, and a valve body are placed in a substantially cylindrical body in order from one end along its axis. By arranging and fixing an operating rod at the center of each of the diaphragms and plate valves, these diaphragms and valve bodies can be interlocked, and there is a gap between the first diaphragm and the bottom plate at one end of the cylindrical body. A first chamber, a second chamber between the first diaphragm and the second diaphragm, a third chamber between the second diaphragm and the third diaphragm, and a third chamber between the third diaphragm and the valve body. A fifth chamber is provided between the plate valve and the bottom plate at the other end of the cylindrical body, and a gas inlet and a gas outlet are provided in the cylindrical body. The gas can be introduced and the raw gas in the fifth chamber can be supplied to the gas burner section through the gas outlet, and the first chamber and the outlet side of the nozzle can be connected through a first continuous passage. The fifth chamber and the inlet side of the nozzle are communicated via a gas supply pipe, the second chamber and the burner section inlet side are communicated via a second communication passage, and the third chamber is communicated with the inlet side of the nozzle through a second communication passage. and the outlet side of the burner portion are communicated via a third communication passage, and the pressure receiving areas of the first diaphragm, the third diaphragm, and the valve body are made substantially equal, and the pressure receiving area of the second diaphragm is made equal to each other. The area is larger than the pressure receiving area of the first diaphragm, the third diaphragm, and the valve body, and the second communicating passage and the third communicating passage are communicated by a bypass passage, and the second communicating passage and the third communicating passage are connected to each other by a bypass passage. Pressure drop means are installed in either one of the third communication passages and the bypass passage, and at least one of these pressure drop means can be adjusted. 1. The nozzle outlet pressure P is adjusted to the first chamber of the ratio control valve section. The nozzle population pressure P2 can be detected in the fifth chamber, and the pressure difference (P) between the burner section inlet pressure P and the burner section outlet pressure P4
3 P4) can be detected in the second and third chambers. Additionally, the supply gas pressure can be detected in the fourth chamber.

Therefore, the second diaphragm (air differential pressure receiving part) 62 is pushed downward (in the figure) by the differential pressure (P, '-P,) on both sides of the burner part, and as a result, the second diaphragm (air differential pressure receiving part) is pushed downward (in the figure). The plate valve 92 is displaced in the opening direction, and the amount of raw gas flowing to the burner section G increases. Then, the differential pressure Pg - Ps on both sides of the nozzle ("nozzle outlet side and nozzle inlet side", the same applies hereinafter)
increases, the first diaphragm 61 and the plate valve (raw gas differential pressure receiving part) 92 receive pressure, the load on the operating rod 8 in the closing direction of the plate valve 92 increases, and the differential pressure between these two (P3- P,
and Pz Ps) apply loads in opposing directions via the operating rod 8, the operating rod 8 is displaced until these loads are balanced, and the burner side differential pressure receiving section 62 and the nozzle both side differential pressure receiving section The opposing forces of 61°92 converge to a balanced position, and the amount of raw gas is supplied.

At this time, the air ratio is determined only by the physical property constants of gas, air, etc., the fluid constants of the passages, the area ratios of the respective pressure receiving parts, etc., and this air ratio remains constant even if the amount of air changes.

Therefore, if this gas burner device is used, although the air ratio in the gas burner section can be kept constant, the structure of the ratio control valve section is a mere mechanical structure.
Unlike conventional systems, the structure is simpler and the number of parts is reduced, resulting in less maintenance, improved reliability, and lower production costs.

In addition, it can easily respond to sudden changes in air volume such as gusts of wind.
Since there is no need to increase the source pressure of the blower fan, the production cost of the blower fan can be reduced, and furthermore, the generation of noise and the like can be prevented.

Furthermore, the air ratio also has an effect on changes in air volume caused by dirt or dead leaves adhering to the exhaust port (of the heat exchanger inner shell), clogging of the heat exchanger fins, or clogging of the intake system passages and filters. I won't receive it.

The gas burner device according to the present invention is not affected by fluctuations in the supply gas pressure P, since the pressure receiving areas of the third diaphragm and the plate valve are equal.

Furthermore, the second communication passage and the third communication passage are communicated by a bypass passage, and a pressure drop means is installed in either one of the second communication passage or the third communication passage and the bypass passage, respectively. Since at least one of the pressure filling means is adjustable, by varying the pressure drop resistance of one side, the gas differential pressure can be changed and the air ratio can be easily adjusted, making it suitable for various gas fuels and various burners. It can have wide adaptability (versatility).

Therefore, if the ratio control valve device of the present invention is used, it can be easily applied to all kinds of gases.

Note that if a compression spring is interposed between the operating rod and the bottom plate at the other end of the cylinder, and the spring force of this compression spring is adjustable, the compression spring (between the operating rod and the other end of the cylinder) can be adjusted. It is possible to adjust for variations in the spring characteristics of the compression spring (between the bottom plate and the bottom plate), and it is also possible to easily match the air ratio characteristics to the burner.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of an embodiment of the gas burner device according to the present invention, FIG. 2 is an enlarged sectional view taken along line nn in FIG. 1, and FIG. 3 is an enlarged sectional view taken along line mm in FIG. Fig. 4 is a partial cross-sectional view of the second embodiment, Fig. 5 is a view corresponding to Fig. 1 of the third embodiment, Fig. 6 is a partial cross-sectional view of the fourth embodiment, and Fig. 7 is a cross-sectional view of the conventional example. It is a diagram. Ratio control valve part Gas burner part Bypass path Variable throttle part (pressure loss means) Air blowing means (blow fan) Raw gas supply pipe Raw gas nozzle Cylindrical body Bottom plate Bottom plate First diaphragm Second diaphragm Third diaphragm First chamber First communication pipe (No. (Series passage) Second chamber Second communication pipe (Second communication passage) Fixed throttle (Pressure drop means) Third chamber Third communication pipe (Third communication passage) Fixed throttle (Pressure drop means) Fourth chamber Gas introduction pipe No.5 Chamber gas discharge pipe operating rod plate valve (valve body) Gloss 20 Side J Figure 4 Do] 5 B Teeth procedural amendment (method) 1゜Indication of incident 2, title of invention 3, person making the amendment 1999 patent Relationship with Application No. 134196 Gas Burner Device Incident

Claims (2)

[Claims] (1) Comprising a gas burner section, a blowing means, and a ratio control valve section, and supplying raw gas to the gas burner section through the ratio control valve section and the nozzle, and supplying combustion air by the blowing means. In the combustion gas burner device, in configuring the ratio control valve part, a first diaphragm, a second diaphragm, a third diaphragm, and a valve body are arranged in order from one end along the axis of the substantially cylindrical body, and By fixing an operating rod to the center of each of the diaphragms and the valve body, these diaphragms and the valve body can be interlocked, and a first chamber is formed between the first diaphragm and the bottom plate at one end of the cylinder. , a second chamber between the first diaphragm and the second diaphragm, a third chamber between the second diaphragm and the third diaphragm, a fourth chamber between the third diaphragm and the valve body, A fifth chamber is formed between the plate valve and the bottom plate at the other end of the cylinder, and a gas inlet and a gas outlet are provided in the cylinder, and raw gas is introduced into the fourth chamber through the gas inlet. the raw gas in the fifth chamber can be supplied to the gas burner section by the gas discharge port, and the first chamber and the outlet side of the nozzle are communicated via a first continuous passage. The fifth chamber and the inlet side of the nozzle are communicated via a gas supply pipe, the second chamber and the burner section inlet side are communicated via a second communication path, and the third chamber and the burner section are communicated with each other via a second communication passage. and the outlet side of the valve body through a third communicating passage, and the pressure receiving areas of the first diaphragm, the third diaphragm, and the valve body are made substantially equal, and the pressure receiving area of the second diaphragm is made to be the same as that of the first diaphragm. The pressure receiving area of the diaphragm and the third diaphragm and the valve body is larger than that, and the second communicating passage and the third communicating passage are communicated by a bypass passage, and the second communicating passage and the third communicating passage are connected to each other by a bypass passage. A gas burner device characterized in that pressure drop means are installed in either one of the passages and the bypass passage, and at least one of these pressure drop means is adjustable. (2) A compression spring is interposed between the operating rod and the bottom plate at the other end of the cylindrical body, and the spring force of this compression spring is adjustable. The gas burner device described.