JPH04113A - Gas burner device - Google Patents

Abstract

PURPOSE:To keep an air ratio constant even if the amount of air is varied by a method wherein a differential pressure between the outlet side of a burner and the inlet side of the burner dependent on the amount of blown air and another differential pressure between the nozzle outlet and the nozzle inlet dependent on the amount of gas are balanced from each other. CONSTITUTION:As the amount of combustion air is increased, the differential pressure P2-P4 across a burner is increased so as to push the first diagram 61 and the third diagram 63 upwardly, a leaf valve 92 is displaced toward the opening direction through an operating rod 8 and then the amount of live gas flowing toward a burner G is increased. Then, the differential pressure P2-P5 across the nozzle is increased, a load applied in the closing direction of the leaf valve 92 is increased against the operating rod 8. These two differential pressures P3-P4 and P2-P5 apply load through the operating rod 8 in the opposite direction, resulting in that the operating rod 8 is displaced until these loads are balanced and is converged into a position where the opposing forces of the differential pressures receiving parts 61, 63 of the burner and the differential pressure receiving parts of the nozzle are well balanced. Even if the amount of air is varied, this air ratio is kept constant.

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 mixing 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 fed back, and the gas amount and air amount are individually controlled.

On the other hand, conventionally, as shown in FIG. 2, 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 was adopted, which made element conversion and the number of parts in the Fino < Tsuta circuit complicated and large; as a result, Since it takes time and effort to maintain, it lacks reliability, and has the disadvantage of increasing production costs.

(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, when a gust of wind is applied to the exhaust port of the gas burner, the internal pressure of the air chamber A increases even though the air flow rate decreases, so that the operation of the ratio control valve section C is limited to valve 1.
As a result of operating in the direction of opening 4 and changing the air ratio,
A burner with a narrow combustion range, such as an all-primary mixing burner, has the disadvantage that it is difficult to control the air-fuel ratio with high precision while receiving disturbances such as gusts of wind.

An object of the present invention is to provide a gas burner adjustment device that eliminates these disadvantages, improves adjustment accuracy, and can be made more compact.

[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 valve body, and the third diaphragm and fixing the 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 bottom of one end of the cylinder body and the first diaphragm, a second chamber between the first diaphragm and the second diaphragm, a third chamber between the second diaphragm and the valve body, and a third chamber between the second diaphragm and the valve body. A fourth chamber is provided between the third diaphragm and a fifth chamber is provided between the third diaphragm and the bottom of the other end of the cylindrical body, and a gas inlet and a gas outlet are provided in the cylindrical body, The raw gas can be introduced into the third chamber through the gas inlet, and the raw gas in the fourth chamber can be supplied to the gas burner section through the gas outlet, and the first chamber can be placed on the burner outlet side. the fifth chamber communicates with the inlet side of the burner, the second chamber communicates with the outlet side of the nozzle, and the fourth chamber communicates with the inlet side of the nozzle; The effective areas of the second diaphragm and the valve body are made substantially equal, and the effective areas of the second diaphragm and the valve body are made substantially equal.

[Action of the invention]

Since the gas burner device of the present invention is configured as described above, the nozzle outlet pressure P can be detected in the second chamber 72 of the ratio control valve section, and the nozzle population pressure P2 can be detected in the fourth chamber 72.
4, the burner section population pressure P3 can be detected in the fifth chamber 75, and the burner section outlet pressure P4 can be detected in the first chamber 71.

Further, the supply gas pressure P can be detected in the third chamber 73.

Therefore, when the amount of air blown (combustion air amount) is increased, both sides of the burner part G ("burner part outlet side and burner part inlet side")
The first diaphragm 61 and the third diaphragm 63 are actuated by the differential pressure P, -P4 in the upward direction (
) in the figure, and as a result, the valve body (plate valve) 92 is displaced in the opening direction via the operating rod 8, and the amount of raw gas flowing to the burner section G increases. Then, the differential pressure P 2P s on both sides of the nozzle 31 (“nozzle outlet side and nozzle inlet side”, hereinafter the same) increases, and the second diaphragm 62 and the valve body (plate valve) (raw gas differential pressure receiving part) 92 , the load in the closing direction of the valve body (plate valve) 92 increases on the operating rod 8,
Since these two differential pressures (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 differential pressure on both sides of the burner section G is increased. From the pressure receiving part (first diaphragm 61 and third diaphragm 63) and the differential pressure receiving part on both sides of the nozzle (the effective area of the third diaphragm 63 minus the effective area of the valve body 92, and the effective area of the first diaphragm 61) The opposing force of the second diaphragm 62 (subtracting the effective area of the second diaphragm 62) converges 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.

(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 in the upper part of the air chamber case 21. In this case, air chamber case 2
1 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. 3 is a gas supply pipe, and the air chamber case 21
is placed on the bottom of the. 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 protrudes into the mixing chamber M,
Raw gas is ejected into the mixing chamber M through the ejection holes 311311, . 41.41. ... is a through hole, which is formed in the bottom plate of the mixing chamber case 22. This through hole 41
Combustion air (combustion air supplied by the blower fan 21) is supplied into the mixing chamber M via 41, .
Mixed with 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.

S is the cylindrical body S of this invention. Also, 8 is an operating rod,
It is arranged along the axis of the cylinder S. This operating rod 8 can move forward and backward in the axial direction of the cylinder S. Reference numeral 91 denotes an annular valve seat, which is formed on the inner surface of the side wall of the cylindrical body S. Further, 92 is a disc-shaped plate valve (corresponding to the "valve body" of the present invention), which is fixed in the middle of the operating rod 8. The plate valve 92 and the valve seat 91 constitute the valve portion 9.

A first diaphragm 61 is fitted onto the operating rod 8. This first diaphragm 61 is arranged at the large diameter portion 51 of the cylinder S. This first diaphragm 61
A first chamber 71 is formed between the first chamber 71 and the bottom surface of the cylindrical body S. This first chamber 71 is communicated with the inside of the heat exchanger inner shell 23 (corresponding to the "burner section outlet side" of the present invention) by a first communication pipe 711. Therefore, the internal pressure of the first chamber 71 is equal to the internal pressure P4 inside the heat exchanger inner shell 23. A second diaphragm 62 is fitted below the first diaphragm 61 in the operating rod 8. This second diaphragm 62 is arranged in the small diameter portion 53 of the cylinder S, and forms a second chamber 72 between it and the first diaphragm 61. This second chamber 72 is connected to the nozzle 31 by a second communication pipe 721.
It is connected to the exit side. Therefore, the internal pressure of the second chamber 72 is equal to the internal pressure P on the exit side of the nozzle 31. Further, the plate valve 92 is fixed below the large two diaphragms 62 on the operating rod 8, and
A third chamber 73 is formed between the two. A raw gas introduction lower 31 is formed on the side wall of the cylindrical body S in the third chamber 73. Next, 63 is a third diaphragm, which is fixed below the plate valve 92 on the operating rod 8.

This third diaphragm 63 is disposed on the large diameter portion 52 of the cylinder S, and forms a fourth chamber 74 between it and the plate valve 92. A gas discharge lower 41 is formed in this fourth chamber 74 . The pressure receiving area of this plate valve 92 is approximately equal to the pressure receiving area of the second diaphragm 62. The raw gas is introduced into the ratio control valve section C1, that is, the third chamber 73, passes through the valve section 9, enters the fourth chamber 74, and is discharged from the cylindrical body S via the discharge lower 41. The raw gas discharged from the cylindrical body S flows into the mixing chamber M of the gas burner section G via the gas supply pipe 3. The pressure receiving area of the third diaphragm 63 is approximately equal to the pressure receiving area of the first diaphragm 61. A fifth chamber 75 is formed between the third diaphragm 63 and the bottom (lower part) of the cylinder S. This fifth chamber 75 is communicated with the air chamber A (corresponding to the "burner section inlet side" of the present invention) through a fifth communication pipe 751. Therefore, the internal pressure of the fifth chamber 75 is reduced to the air chamber A.
It is equal to the internal pressure P3 of . Note that 632 is a spring seat, which is installed at the bottom (lower part) of the cylindrical body S.

This spring seat 632 can be moved back and forth along the axis by a bolt and nut mechanism 633. Further, 631 is a compression spring, which is installed between the spring seat 632 and the third diaphragm 63. This compression spring 631 is for offsetting the weight of movable parts such as the operating rod 8, the plate valve 92, and the diaphragms 61, 62, 63. In addition, the bolts mentioned above
By adjusting the nut mechanism 633, the compression spring 6
31 spring force can be adjusted.

Therefore, this gas burner device operates as follows.

When the amount of combustion air increases, the differential pressure on both sides of the burner PzP4
becomes larger, pushing the first diaphragm 61 and the third diaphragm 63 upward (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 burner section G is reduced. increases. Then, the differential pressure P, -P on both sides of the nozzle ("nozzle outlet side and nozzle inlet side", the same applies hereinafter) increases, and the second diaphragm 62 and the valve body (plate valve) (raw gas difference summer pressure receiving part) 92 The load in the closing direction (downward) of the plate valve 92 increases on the operating rod 8 via the operating rod 8, and these two differential pressures (P3P4 and PzPs) apply loads in opposite directions via the operating rod 8. Therefore, operating rod 8
is displaced until these loads are balanced, and the burner section both side differential pressure receiving sections 61 and 63 and the nozzle both side differential pressure receiving section (the effective area of the third diaphragm 63 minus the effective area of the valve body 92, and The opposing force (the area obtained by subtracting the effective area of the second diaphragm 62 from the effective area of the first diaphragm 61) converges 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,
The pressure receiving area of the first diaphragm 61 and the third diaphragm 63 is S, the pressure receiving area of the second diaphragm 62 and the valve body 92 is St, and the upward direction of the load applied to the diaphragm and the plate valve is positive. Note that the supply gas pressure is P
Let it be l.

(1), Load applied to the gas-related first diaphragm p,,s, ... ■Load applied to the second diaphragm PI St PS St ... ■Load applied to the plate valve PI St +P2 St ... ■Third The load applied to the diaphragm, -P2S, ... ■ ■+■±■+■ is (S, -3z) (ps-P2) ... ■ (2), The load applied to the air-related first diaphragm -P , S, ... ■ Load applied to the third diaphragm P, S, ... ■ ■+■ is S, (P3 P4)... ■ The difference in load between the above ■ and the above [phase] is the opening/closing of the valve part. These become forces and are displaced until they are balanced. Therefore, in the equilibrium state, ■--■ becomes (P2-ps)/(P3-P,)-3t/(St Sz), and the ratio between the gas differential pressure and the air differential pressure becomes a constant, and as a result , even if the air amount is changed, the raw gas amount changes while the air ratio remains constant.

〔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 valve body, and a third diaphragm are sequentially placed in a substantially cylindrical body along its axis from one end. At the same time, by 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 a first diaphragm is formed between the bottom of one end of the cylinder body and the first diaphragm. one chamber, a second chamber between the first diaphragm and the second diaphragm, a third chamber between the second diaphragm and the valve body, and a fourth chamber between the valve body and the third diaphragm. A fifth chamber is defined between the third diaphragm and the bottom of the other end of the cylindrical body, and a gas inlet and a gas outlet are provided in the cylindrical body, and the gas inlet allows gas to be generated in the third chamber. The gas can be introduced and raw gas in the fourth chamber can be supplied to the gas burner section through the gas outlet, and the first chamber can be communicated with the outlet side of the burner, and the fifth chamber can be connected to the burner outlet side. The second chamber is communicated with the outlet side of the nozzle, and the fourth chamber is communicated with the inlet side of the nozzle, and the effective areas of the first diaphragm and the third diaphragm are made substantially equal. Since the effective areas of the second diaphragm and the valve body are made substantially equal, the nozzle outlet pressure P can be detected in the second chamber 72 of the ratio control valve section, and the nozzle inlet pressure P2 can be detected in the fourth chamber 7.
4, the burner section inlet pressure P3 can be detected in the fifth chamber 75, and the burner section outlet pressure P4 can be detected in the first chamber 71.

Further, the supply gas pressure P1 can be detected in the third chamber 73.

Therefore, when the amount of air blown (combustion air amount) is increased, the first diaphragm 61 and The third diaphragm 63 is actuated and pushed upward (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 burner section G increases. Then, the differential pressure P2-P on both sides of the nozzle 31 (“nozzle outlet side and nozzle inlet side”, the same applies hereinafter),
increases, and the load in the closing direction of the plate valve 92 increases on the operating rod 8 via the second diaphragm 62 and the plate valve (raw gas differential pressure receiving part) 92, and these two differential pressures (P3 P
4 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 section G both sides differential pressure receiving section (first diaphragm 61 and From the effective area of the three diaphragms 63) and the nozzle side differential pressure receiving part (the third diaphragm 63)
2 minus the effective area and the first diaphragm 6
1 minus the effective area of the second diaphragm 62) converges 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 the conventional method, the structure is simpler and the number of parts is reduced, resulting in improved reliability with less maintenance 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.

Moreover, since the first diaphragm and the third diaphragm are arranged symmetrically, when the same accuracy is required as compared to the device already filed by the applicant (Japanese Patent Application No. 1-134196), The diameters of these diaphragms can be made small, while accuracy can be further improved if diaphragms of the same diameter are used.

[Brief explanation of drawings]

FIG. 1 is a sectional view of an embodiment of a gas burner device according to the present invention, and FIG. 2 is a sectional view of a conventional example. S...61...62...63...71...72...73...731...74...741...75...8...92 ... Cylindrical body First diaphragm Second diaphragm Third diaphragm First chamber Second chamber Third chamber Gas inlet Fourth chamber Gas discharge pipe Fifth chamber Operating rod plate valve (valve body) C... Ratio control valve part G... Gas burner section 24... Air blowing means (air blowing fan) 31...
・ Raw gas nozzle

Claims (1)

[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 valve body, and a third diaphragm 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 bottom of one end of the cylinder body and the first diaphragm. A second chamber is between the first diaphragm and the second diaphragm, a third chamber is between the second diaphragm and the valve body, a fourth chamber is between the valve body and the third diaphragm, and a fourth chamber is between the valve body and the third diaphragm. A fifth chamber is defined between the third diaphragm and the bottom of the other end of the cylindrical body, and a gas inlet and a gas outlet are provided in the cylindrical body, and raw gas is introduced into the third chamber through the gas inlet. The raw gas in the fourth chamber can be supplied to the gas burner section through the gas outlet, and the first chamber is connected to the outlet side of the burner, and the fifth chamber is connected to the inlet side of the burner. the second chamber communicates with the outlet side of the nozzle and the fourth chamber communicates with the inlet side of the nozzle, the effective areas of the first diaphragm and the third diaphragm are substantially equal, and the second chamber communicates with the outlet side of the nozzle. A gas burner device characterized in that the effective areas of a diaphragm and the valve body are approximately equal.