JPH0367916A - Gas burner - Google Patents

Abstract

PURPOSE:To make it possible to control constant the ratio of air with respect to the volume of a raw gas all the time by dividing a ratio control valve section by three diaphragms and one valve body and providing five separated chambers and communicating each chamber with both sides of a burner section and both sides of a nozzle and opening and closing the valve body by the pressure difference. CONSTITUTION:A gas burner device detects the outlet pressure P5 of a nozzle by a first chamber 71 of a ratio control valve section C and at the same time detects the inlet pressure P2 of the nozzle by a fifth chamber 75, and the inlet pressure P3 of a burner section is detected by a second chamber 72, and the outlet pressure P4 of the burner section is detected by a third chamber 73. With this arrangement when the blast volume is increased, a diaphragm 62 is pushed downwards by the pressure difference (P3 - P4) on both sides of the burner section and a plate valve 92 is displaced through a working rod 8 in the direction in which the valve opens and the volume of a raw gas that flows to the burner section G increases. Then, the pressure differences (P2 - P5) on both sides of the nozzle is increased, a diaphragm 61 and a valve body 92 are under pressure, and a load to the working rod 8 in the direction in which the valve body 92 is closed is increased, and those two pressure differences exert load through the working rod in opposite directions so that the working rod 8 is displaced until those loads are balanced, and the supply of the raw gas is made.

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 a gas burner such as a water heater that proportionally controls the combustion load is operated using the all-primary combustion method, the quality of the 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 the gas amount and air amount are individually controlled while performing feedbanking.

On the other hand, conventionally, as shown in FIG. 7, three diaphragms 1112.13 and a valve body 14 are configured to be linked (in the vertical direction) as a ratio control valve section C, and the diaphragm 11 detects the fan pressure of the combustion air in the gas burner G, thereby controlling the secondary pressure of the raw gas supplied to the gas burner section G. , exists.

[Problem to be solved by the invention]

However, in the former case, (]), electronic control was adopted, which made element conversion and the number of parts in the foot bank circuit complicated and large, resulting in poor reliability due to the high maintenance time. Moreover, it has the disadvantage that the production cost becomes high.

(2) In order to minimize the change in air volume due to gusts of wind, etc., it is necessary to increase the original pressure of combustion air, so it is necessary to increase the rotation speed of the blower fan or increase the fan diameter. Therefore, 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 blade 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 has the disadvantage that it is difficult to control the air ratio constantly to the raw gas amount.

Second, 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 to close the valve 14. As a result, it is difficult to control the air-fuel ratio with high precision in the face of external disturbances such as gusts of air in a burner with a narrow combustion range, such as an all-primary mixer burner. It was inconvenient.

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 raw gas is supplied to the gas burner section through the ratio control valve section and the nozzle. In a forced combustion θ) gas burner device in which combustion air is supplied by the air blowing means, the ratio control valve section is configured such that a substantially circular cylindrical body is provided with combustion air from one end along its axis. A first diaphragm, a second diaphragm, a first mod diaphragm, and a valve body are arranged, and an operating rod is fixed at the center of each of the diaphragms and the valve body, so that these diaphragms and the valve body can be interlocked, and a first chamber 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, and a second chamber between the second diaphragm and the third diaphragm. a third chamber, a fourth chamber between the third diaphragm and the plate valve, a fifth chamber between the valve body and the bottom plate at the other end of the cylinder, and gas introduction rl into the cylinder.
and a gas exhaust port are provided, and this gas introduction [1 through 5. to allow raw gas to be introduced into the fourth chamber, and to supply raw gas from the fifth chamber to the gas burner section by the gas outlet, and to connect the first chamber to the outlet side of the nozzle. The fifth chamber and the inlet side of the nozzle are communicated with each other, and the second chamber and the inlet [1 side of the burner section are communicated with each other, and the third chamber and the outlet I side of the burner section are communicated with each other. and the first diaphragm, the three diaphragms and i
'+ii The effective area of the integrated valve is approximately equal to 2, and the effective area of the second diaphragm is made smaller than the effective area of the first diaphragm, the three diaphragms, and the valve body.

Furthermore, in the gas burner device according to the second aspect, due to the structure of the burner section (a structure in which the pressure loss in the passage from the mixing chamber to the combustion chamber is set to be so small as to be negligible compared to the secondary gas pressure P2Q).
What is the internal pressure P of the mixing chamber (nozzle outlet side) M? :! In some cases, the internal pressure in the inner cylinder 23 is approximately equal to 1 to 7, and the first communication passage 711 is merged with the third communication passage 731, and the mixing chamber (nozzle exit side) M is The internal pressure P4 inside the Jino I Tsunai 111423 is adopted as the internal pressure (■).

3 4 Further, in the gas burner device of the third claim, the burner outlet pressure P4 is considered to be equal to atmospheric pressure due to the configuration of the burner section, and the third chamber 73 is opened to the atmosphere.

Further, in the gas burner device of the fourth claim, due to the configuration of the burner section, the burner outlet pressure P4 and the nozzle outlet pressure P are considered to be equal to atmospheric pressure, and the first chamber and third chamber 73 are at atmospheric pressure. It is open inside.

Further, in the gas burner device according to the fifth aspect, due to the structure of the burner section, the burner section inlet pressure P3 is considered to be equal to the atmosphere, and the second chamber 72 is opened to the atmosphere.

[Action of the invention]

Since the gas burner device according to the first aspect is configured as described above, the nozzle outlet pressure P5 can be detected in the first chamber 71 of the ratio control valve section, and the nozzle pressure P5 can be detected in the first chamber 71 of the ratio control valve section. It can be detected in the fifth chamber, the bar section population pressure P3 can be detected in the second chamber, and the bar section outlet pressure P4 can be detected in the third chamber.

Additionally, the supply gas pressure can be detected in the fourth chamber.

Therefore, when the amount of air blown (combustion air amount) is increased, the second diaphragm (air The differential pressure receiving part) 62 is pushed out in the f direction (in the figure), and as a result, the plate valve 92 is displaced in the opening direction via the operating rod 8, and the amount of raw gas flowing to the banner part G increases. As a result, the differential pressure P2-P5 on both sides of the nozzle (the nozzle outlet side and the nozzle inlet side 1, hereinafter the same) increases, and the first diaphragm 1, 61 and the valve body (plate valve) (raw gas differential pressure receiving part)
92 receives pressure, the load on the operating rod 8 in the closing direction of the valve body 92 increases, and the differential pressure between these two (P3 Pa and P2
P5) apply loads in opposing directions via the operating rod 8, so the operating rod 8 is displaced until these loads are balanced, and the burner side differential pressure receiving section 62 and the nozzle side differential pressure receiving section 61゜92 The opposing forces of the two converge to a balanced position, and the amount of raw gas is supplied.

5 When 1, the air ratio is determined only by the physical property constants of the gas and air amount, the fluid constants of the passage, the area ratio of each pressure receiving part, etc., and even if the air amount changes, this air ratio remains constant. Become.

Further, the gas burner device according to the second claim has the following features:1. Due to the design of the burner section, the internal pressure P of the mixing chamber (nozzle exit side) M.

In this case, it is assumed that the internal pressure P4 in the heat exchanger inner shell 23 is approximately equal to the internal pressure P4 in the heat exchanger inner shell 23, and the first communication passage 711 is merged with the third communication passage 731, and the internal pressure P in the mixing chamber (nozzle outlet side) is The internal pressure P in the internal cylinder 23 is adopted. In this case, since the first chamber 71 communicates with the third chamber 73, the setting of the communication path can be simplified.

In the gas burner device according to the third aspect, the burner outlet pressure P4 is considered to be equal to atmospheric pressure due to the design of the burner section, and the third chamber 73 is opened to the atmosphere. In this case, since a communication pipe connecting the bar outlet side and the third chamber 73 is not required, the setting of the communication path can be simplified.

Further, in the gas burner device according to the fourth aspect, the burner outlet pressure P4 and the nozzle outlet pressure P are considered to be equal to atmospheric pressure due to the design of the burner section, and the first chamber and the third chamber 73 are at atmospheric pressure. It is open inside. in this case,
Since a communication pipe connecting the burner outlet side and the third chamber 73 and the first chamber is not required, the setting of the communication path can be simplified.

In the gas burner device according to the fifth aspect, the burner section inlet pressure P3 is considered to be equal to the atmosphere due to the design of the burner section, and the second chamber 72 is opened to the atmosphere. In this case, there is no need for a communication pipe that communicates the second chamber 72 with the burner section inlet side, so the setting of the communication path can be simplified.

[Explanation of Examples]

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

In FIG. 1, G is the gas burner part of the gas water heater 1, and C
is the 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 in the air chamber case 21, and 23 is a heat exchanger inner shell installed above the air chamber case 78. in this case,
An air chamber is formed between the air chamber case 21 and the mixing chamber case 22, 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. Reference numeral 31 denotes a nozzle, which is provided to protrude from the gas supply pipe 3. This nozzle 31 is connected to the mixing chamber M
The raw gas is ejected into the mixing chamber M through the ejection holes 311311, . 41,41. . . . is a through hole 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 4141, . . . 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 also a mixed gas (a mixture of raw gas and combustion air, hereinafter referred to as a mixture).
This equalizes the pressure.

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

, , -(7) The 71L combined gas is injected into the heat exchanger inner shell 23 through the pores 431 , 431 , . . . 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 includes 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 shaped like 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 59 0 . 91 is an annular valve seat;
It is formed on the inner surface of the side wall of the cylindrical body 5.

Reference numeral 92 denotes a disk-shaped plate valve, which is fixed to the tip (lower end) of the operating rod 8 with a bolt 81. The valve portion 9 is laterally S-&ed by the plate valve 92 and the valve seat 91. 93
is a spring seat, and the bolt 81 is connected to the plate valve 92.
It is collinear with . 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 931 is connected to the operating rod 8 and the plate valve 9.
This is to offset the weight of movable parts such as 2 and diaphragms 61, 62, and 63, which will be described later. Note that a fifth chamber 75 is formed between the valve portion 9 and the bottom plate 52.

A third diaphragm 63 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. In addition, this third diaphragm 6
3 has the same pressure receiving area as the plate valve 92. Reference numeral 62 denotes a second diaphragm, which is pushed into the operating rod 8i, ;Z through a tubular spacer 83. This second diaphragm 62 is installed in the large diameter portion 53 within the cylindrical body 5. This third diaphragm 62 is connected to the third diaphragm 1.6.
3, and a third chamber 73 is formed between the third diaphragm 63 and the third diaphragm 63. This third chamber 73
is communicated with the inside of the heat exchanger inner shell 23 (corresponding to the "burner section outlet side" of the present invention) through a third communication pipe 731. Therefore, the internal pressure of the third chamber 73 is equal to the internal pressure P4 inside the heat exchanger inner shell 23. Reference numeral 61 denotes a first diaphragm, which is fitted into the operating rod 8 via a tubular smoother 84. This first diaphragm 61 is disposed above the second diaphragm 62 (in FIG. 1) and forms a second chamber 72 between it and the second diaphragm 62,
A first chamber 71 is formed between the bottom plate (of the cylindrical body 5) 51.

The second chamber 72 is communicated with the air chamber A (corresponding to the "burr section inlet side" of the present invention) through a second communication pipe 721. Therefore, the internal pressure of the second chamber 72 is equal to the internal pressure P3 of the air chamber A. Further, the first chamber 71 is communicated with the outlet side of the nozzle 31 through a first 1 2 communication pipe 711 . Therefore, the internal pressure of the first chamber 71 is reduced by the nozzle 31.
The internal pressure on the outlet side is equal to P5. 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 part C1, that is, the fourth chamber 74, through the raw gas inlet 741, and after passing through the valve part 9, enters the fifth chamber 75, and is discharged into the cylindrical body through the outlet 751. 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.

Therefore, this gas burner device operates as follows.

When the amount of combustion air increases, the differential pressure on both sides of the burner P3P
a increases, 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, and the amount of raw gas flowing to the banner portion G increases. Then, the differential pressure P 2 P s on both sides of the nozzle (“nozzle outlet side and nozzle inlet side”, hereinafter referred to as “between”) increases, and the first diaphragm 61 and the plate valve (raw gas differential pressure receiving part) 92 receive the 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-P4 and P
'x P s ) apply loads in opposing directions via the operating rod 8, so the operating rod 8 is displaced until these loads are balanced, and the burner side differential pressure receiving section 62 and the nozzle 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. 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, and C is the pressure receiving area ratio (large diaphragm area 3 4 /small diaphragm area) (C>1), and the load applied to the diaphragm and plate valve. The upward direction is positive.

(1), Loads applied to the gas-related first diaphragm P, S ... ■ Loads applied to the third diaphragm P, S ... ■ Loads applied to the plate valve P, S-P, S ... ■ ■1 -■→-■, (P2-P5)S ... ■ (2), Load applied to the air-related first diaphragm P3S ... ■ Load applied to the second diaphragm P, cs-p3cs ... ■ Second Load applied to the three diaphragms P4S ... ■ ■→-■→-■, (P4 -P3) (C-1) S... ■The difference in load between the above ■ and the above ■ becomes the valve opening/closing force. These are displaced until they are balanced. Therefore, in equilibrium, ■−−■
Then, (P2-p=,)/(P:]-P4)=C-1, and the ratio of the gas differential pressure to the air differential pressure becomes a constant C1. As a result, even if the air amount is changed, the air The amount of raw gas changes while the ratio remains constant.

FIG. 2 shows an embodiment of the second claim. In this embodiment, due to the configuration of the bar part (a configuration in which the pressure loss in the passage from the mixing chamber to the combustion chamber is negligibly small compared to the secondary gas pressure P2), the mixing chamber (nozzle exit side) M
This is a case where the internal pressure P5 in the heat exchanger inner shell 23 is considered to be approximately equal to the internal pressure P4 in the heat exchanger inner shell 23, and the first communication passage 711 is connected to the third communication passage 7.
31, and the internal pressure P of the mixing chamber (nozzle outlet side) M,
The internal pressure P4 inside the heat exchanger inner shell 23 is adopted as the internal pressure P4.

FIG. 3 shows an embodiment of the third claim. In this example, due to the structure of the gas burner, the internal pressure of the heat exchanger inner shell 23 (burner outlet side pressure P, l) is considered to be about the same as atmospheric pressure, and the Torso 2
3 and the third chamber 73 are open to the atmosphere.

FIG. 4 is an embodiment of the fourth claim, in which the internal pressure of the heat exchanger inner shell 23 (bar outlet side pressure P4) and the mixing chamber M pressure (nozzle outlet side pressure p,) are considered to be approximately the same as atmospheric pressure. In this case, the inside of the heat exchanger inner shell 23, the first chamber 71, and the third chamber 73 are open to the atmosphere.

FIG. 5 shows an embodiment of the fifth claim, in which an exhaust fan E is used, and since the fan inlet pressure (burner population pressure) is equal to atmospheric pressure, the second chamber 72 is opened to the atmosphere. can do. Therefore, the second communication pipe 721 becomes unnecessary.

FIG. 6 shows another 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. The reason why the compression spring 552 can be adjusted by screwing the adjustment bolt 55 is that: (1) fine adjustment can be made to accommodate variations in the spring characteristics of the compression spring (for offsetting the weight of the movable part) 931; In order to make ■,
This is to adapt the air ratio characteristics to the burner. Note that this embodiment can be applied to any of the embodiments of the first to fourth claims.

〔Effect of the invention〕

The gas barge device of the present invention includes a gas burner section, a blowing means, and a ratio control valve section, and raw gas is supplied to the gas burner section through the ratio control valve section and the nozzle, and combustion air is supplied to the gas burner section through the ratio control valve section and the nozzle. In a forced combustion gas burner device that supplies In constructing the ff1l valve section, 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 each of the above-mentioned diaphragms and By fixing an operating rod at the center of the valve body, these diaphragms and the valve body can be interlocked, and a first chamber and a first diaphragm are connected between the first diaphragm and the bottom plate at one end of the cylinder body. and the second diaphragm, a third chamber between the first diaphragm and the third diaphragm, a fourth chamber between the third diaphragm and the valve body, and a fourth chamber between the plate valve and the valve body. The space between the other end of the cylindrical body and the bottom plate is a fifth chamber, and the cylindrical body is provided with a gas inlet and a gas outlet, and the raw gas can be introduced into the fourth chamber through the gas inlet, and the raw gas can be introduced into the fourth chamber. The raw gas in the fifth chamber can be supplied to the gas burner section through a gas discharge port, and the first chamber and the outlet side of the nozzle are communicated with each other, and the fifth chamber and the inlet side of the nozzle are communicated with each other. the second chamber communicates with the inlet side of the bar section, and the third chamber communicates with the outlet side of the bar section, and the first diaphragm, the three diaphragms, and the plate The pressure receiving area of the second diaphragm was made substantially equal to that of the valve, and the pressure receiving area of the second diaphragm was made larger than the pressure receiving area of the first diaphragm, the three diaphragms, and the plate valve, so that the nozzle outlet pressure P5 was adjusted to the ratio control valve part. The nozzle inlet pressure P2 can be detected in the fifth chamber, the burner part inlet pressure P3 can be detected in the second chamber, and the burner part inlet pressure P3 can be detected in the second chamber.
] Pressure P can be detected in the third chamber.

Additionally, the supply gas pressure is detected in the fourth chamber.

Therefore, the second diaphragm (air differential pressure receiving part) 62 is pushed downward (> in the figure) by the differential pressures P and -P4 on both sides of the burner part, and as a result, the plate valve 92 is pushed out via the operating rod 8. It is displaced in the opening direction, and the amount of raw gas flowing to the burner section G increases. As a result, the differential pressure P2-PS on both sides of the nozzle ("nozzle outlet side and nozzle inlet side", hereinafter referred to as "interval") 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 direction of closing the plate valve 92 increases, and these two differential pressures (P39 0 P4 and P2 PS) apply loads in opposite directions via the operating rod 8, so the operating rod 8 These loads are displaced until they are balanced, and the opposing forces within the burner section (jl, +1 differential pressure receiving section 62 and nozzle side differential pressure receiving section 6) and 92 converge in a balanced position, and the amount of raw gas is supplied. be exposed.

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

Therefore, although the air ratio in the gas burner section can be kept constant by using this gas burner device, the ratio control valve section is simply a mechanical structure.
Unlike conventional products, it is easier to take over 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.

Further, in the gas burner device of the second claim, due to the design of the burner section, the internal pressure P5 of the mixing chamber (nozzle outlet side) M is lower than the heat exchanger inner shell 23.
This is a case where the internal pressure in the mixing chamber (
The internal pressure P4 inside the heat exchanger inner shell 23 is adopted as the internal pressure P5 of the nozzle exit side) M. In this case, since the first chamber 71 communicates with the third chamber 73, the setting of the communication path can be simplified.

Further, the gas burner device according to the third aspect is a case in which the burner outlet pressure P4 is considered to be equal to the atmospheric pressure due to the design of the burner section, and the third chamber 73 is opened to the atmosphere. In this case, since a communication pipe connecting the bar outlet side and the first chamber 73 is not required, the setting of the communication path can be simplified.

Further, in the gas burner device of the fourth claim, the burner outlet pressure P4 and the nozzle outlet pressure P5 are considered to be equal to atmospheric pressure due to the design of the burner section, and the first chamber and the third chamber 7
3 was released while it was popular. In this case, a communication pipe connecting the burner outlet side with the third chamber 73 and the first chamber is not required, so that the setting of the communication path can be simplified.

Further, the gas burner device according to the fifth aspect is a case in which the burner section inlet pressure P3 is considered to be equal to the atmosphere in the design of the burner section, and the second chamber 72 is opened during operation. In this case, there is no need for a communication pipe that communicates the second chamber 72 with the burner section inlet side, so the setting of the communication path can be simplified.

[Brief explanation of drawings]

FIG. 1 is a sectional view of an embodiment of the gas burner device according to the present invention, FIG. 2 is a sectional view of an embodiment of the gas burner device of the second claim, and FIG. 3 is a sectional view of an embodiment of the gas burner device of the third claim. 4 is a sectional view of an embodiment of the gas burner device according to claim 4, FIG. 5 is an analytical side view of an embodiment of the gas burner device according to claim 5, and FIG. Partial sectional view, FIG. 7 is a sectional view of a conventional example. Ratio control valve part Gas burner part Air blowing means (blow fan) Raw gas nozzle Cylindrical body Bottom plate Bottom plate First diaphragm Second diaphragm 3 4 Third diaphragm First chamber Second chamber Third chamber Fourth chamber Gas inlet pipe Fifth chamber Gas discharge pipe Operating rod plate valve 5 Figure 2 JP-A-6791.6 (13) Figure 1 Procedural amendment (method) 1. Display of case 1999 patent side No. 203592 2,
Title of the invention: Gas burner device 3, relationship with the amended case Patent applicant address: 1370 Kadoya, Hamaoka-cho, Ogasa-gun, Shizuoka Prefecture Name: Aiken Kogyo Co., Ltd. Representative: Sansei Kono 4, Agent Address: 430 Motoshiro, Hamamatsu City, Shizuoka Prefecture Town 218-29 5, Date of amendment order: November 28, 1 year 6, Subject of amendment Drawing 7, Contents of amendment (1), Engraving of the drawing originally attached to the application (shipment date) ・As shown in the attached sheet

Claims (5)

[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 through the gas outlet, and the first chamber and the outlet side of the nozzle communicate with each other, and the fifth chamber and the nozzle communicate with each other. the second chamber communicates with the inlet side of the burner section, the third chamber communicates with the outlet side of the burner section, and the first diaphragm, the three diaphragms, and the A gas burner device characterized in that the effective areas of the valve bodies are approximately equal, and the effective area of the second diaphragm is larger than the effective areas of the first diaphragm, the three diaphragms, and the valve body. (2) A forced gas burner, comprising a gas burner section, a blowing means, and a ratio control valve section, 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 valve body 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 through the gas outlet, and the fifth chamber communicates with the inlet side of the nozzle;
The second chamber communicates with the inlet side of the burner section, and the third chamber and the first chamber communicate with the outlet side of the burner section, and the first diaphragm, the three diaphragms, and the valve body communicate with each other. A gas burner device characterized in that the effective areas are substantially equal and the effective area of the second diaphragm is larger than the effective areas of the first diaphragm, the three diaphragms, and the valve body. (3) A forced gas burner unit, comprising a gas burner unit, a blower unit, and a ratio control valve unit, supplying raw gas to the gas burner unit via the ratio control valve unit and the nozzle, and supplying combustion air by the blower unit. 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 valve body 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 through the gas outlet, and the first chamber and the outlet side of the nozzle communicate with each other, and the fifth chamber and the inlet of the nozzle communicate with each other. The second chamber communicates with the burner section inlet side, and the third chamber is opened to the atmosphere, and the effective areas of the first diaphragm, the three diaphragms, and the valve body are approximately equal. At the same time, the gas burner device is characterized in that the effective area of the second diaphragm is larger than the effective area of the first diaphragm, the three diaphragms, and the valve body. (4), 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 valve body 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 through the gas discharge port, and the fifth chamber and the inlet side of the nozzle communicate with each other, and the second chamber and the inlet of the burner section The first diaphragm and the third chamber are opened to the atmosphere, and the effective areas of the first diaphragm, the three diaphragms, and the valve body are approximately equal, and the effective area of the second diaphragm is made equal to each other. A gas burner device characterized in that the effective area is larger than the effective area of the first diaphragm, the third diaphragm, and the valve body. (5), 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 valve body 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 through the gas outlet, and the first chamber and the outlet side of the nozzle communicate with each other, and the fifth chamber and the inlet of the nozzle communicate with each other. the third chamber communicates with the burner outlet side, the second chamber is opened to the atmosphere, and the effective areas of the first diaphragm, the three diaphragms, and the valve body are A gas burner device characterized in that the effective areas of the second diaphragm are made substantially equal and larger than the effective areas of the first diaphragm, the three diaphragms, and the valve body.