JPH0367917A - Gas burner - 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 a gas burner in a water heater or the like in which the combustion load is proportionally controlled is operated using the full-secondary 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 the gas amount and air amount are individually controlled while checking the combustion state.

On the other hand, in the past, as shown in FIG. 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 the combustion air in the gas burner G.

[Problems to be solved by the invention] However, as for the part name, (1), since electronic control is adopted, element conversion and the number of parts in the feed hassock circuit become complicated and large, resulting in maintenance problems. Since it takes time and effort, it is not reliable and has the disadvantage of increasing production cost.

In addition, (2) it is necessary to increase the source pressure of combustion air in order to minimize changes in air volume due to gusts of wind, etc."-1 It is necessary to increase the rotation speed of the ventilation fan or increase the fan diameter. As a result, the production cost of the blower fan becomes high, and there are also disadvantages in that noise and the like are 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.

Moreover, when a gust of wind hits the exhaust port of the gas burner,
Although the air flow rate decreases, the internal pressure to the air chamber increases, so the ratio control valve section C operates in the direction of opening the valve 14, changing the air ratio, and as a result, all primary mixing burners For those with a narrow combustion range, such as the above, 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 solve the above problem, 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 the forced combustion gas burner device, in which combustion air is supplied by the blowing means, in configuring the ratio control valve section, a first diaphragm, a second diaphragm, and a second diaphragm are arranged in a substantially cylindrical body along its axis in order from one end. By arranging the second diaphragm, the third diaphragm, and the valve body, 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 first diaphragm and the valve body can be interlocked. A first chamber exists between the bottom plate at one end of the cylinder, a second chamber exists between the first diaphragm and the second diaphragm, a third chamber exists between the first diaphragm and the third diaphragm, and the third chamber exists between the first diaphragm and the third diaphragm. The space between the three diaphragms and the valve body is a fourth chamber, and the space between the valve body and the bottom plate at the other end of the cylinder body is a fifth chamber, and the cylinder body is provided with a gas inlet and a gas discharge port. The raw gas can be introduced into the fourth chamber through the gas inlet, and the raw gas in the fifth chamber can be supplied to the gas burner section through the gas discharge I, and the first chamber and the nozzle The fifth chamber and the inlet side of the nozzle are communicated with each other through a gas supply pipe, and the second chamber and the burner inlet side are communicated with each other through a second communication passage. communicating via a passage, and communicating the first chamber and the outlet side of the bar portion via a third communicating passage, and 1. The effective areas of the first diaphragm, the third diaphragm, and the valve body are approximately equal, and the effective area of the second diaphragm is larger than the effective area of the first diaphragm, the third diaphragm, and the valve body, and In the second communication passage, the total pressure near the fan on the inlet side of the bar can be detected, and the detected total pressure can be adjusted.

[Action of the invention]

Since the gas burner device according to this description 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. The differential pressure between the burner section population pressure I]3 and the burner section outlet pressure P4 can be detected.
P3 P4) can be detected in the second and third chambers. Also,
Feed gas pressure can be detected in the fourth chamber.

Therefore, when the amount of air blown (air amount for baking) is increased, the second diaphragm ( The 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 amount of raw gas flowing to the heena part 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, the load on the operating rod 8 in the closing direction of the plate valve 92 increases, and the differential pressure between these two (P: IF5 etc. p2-p, ,
> apply loads in opposite directions via the operating rod 8, the operating rod 8 is displaced until these loads are balanced.
The opposing forces of the burner side differential pressure receiving section 62 and the nozzle side differential pressure receiving sections 61 and 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.

Further, adjusting the dynamic pressure received to the second communication passage,
By adjusting the differential pressure applied to the second diaphragm 62, the air ratio can be easily adjusted.

(Explanation of Examples) Embodiments of the present invention will be described below based on the drawings.

In FIG. 1, G is the gas tank part of the gas water heater 1, and C is the ratio control valve part.

First, the cassette part G will be explained.

21 is an air chamber case, 22 is a mixing chamber case installed inside the air chamber case 2, and 23 is a heat exchanger inner shell installed above the air chamber case 21. In this case, the air chamber case 21
An air chamber A is formed between the mixing chamber case 22 and the mixing chamber case 22, and a mixing chamber M is formed inside the mixing chamber case 22. Reference numeral 24 is 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. Note that this blower fan does not correspond to the "fan" referred to in this invention. “Fans” of this invention are referred to here as “
It corresponds to the ``impeller'' in ``Blower Fan''. Reference numeral 25 denotes a pressure detection tube, which is installed in the blower pipe 241 of the blower fan 24 . Details of this pressure receiving pipe 25 will be described later. 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 through the gas supply pipe 3. Reference numeral 31 denotes a nozzle, which is provided in a protruding manner on the gas supply pipe 3.

This nozzle 31 protrudes into the mixing chamber M, and the ejection hole 31
1.311. Raw gas is spouted into the mixing chamber M through... 4141. . . are through holes formed in the bottom plate of the mixing chamber case 22. This through hole 4L
4.1. Combustion air (combustion air supplied by the blower fan 21) is supplied into the mixing chamber M through... 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 current plate 42 maintains a mixing space and equalizes the pressure of the mixed gas (a mixture of raw gas and combustion air, hereinafter referred to as a mixture). Reference numeral 43 denotes a flame hole plate, which is installed at the open end of the mixing chamber case 22. Also, 431431,・
... 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. The heat exchanger 44 is composed of a water pipe 441 and fins 442, 4, 42, . . . , and heats water passing through the water pipe 441 using 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. 8 is 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 plate valve 92 and the valve seat 91 constitute the valve portion 9. 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 1 2 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. Note that the effective area of this third diaphragm 63 is equal to the effective area of the plate valve 92. 62 is a second diaphragm, which connects the operating rod 8 through a tubular spacer 83.
is inserted into. This second diaphragm 62 is installed in the large diameter portion 53 within the cylindrical body 5. The effective area of the second diaphragm 62 is larger than the effective area of the third diaphragm 63. This second diaphragm 62 forms a third chamber 73 between it and the third diaphragm 63.

This third chamber 73 is connected to the inside of the heat exchanger inner shell 23 by a third communication pipe 731 (corresponding to the "burner outlet side" of the present invention).
It is communicated with. 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 spacer 84. This first diaphragm 61
is above the second diaphragm 62 (in FIG. 1)
A second chamber 7 is disposed between the second diaphragm 62 and the second diaphragm 62.
2 and a first chamber 71 between the bottom plate (of the cylinder 5) 51 and the bottom plate (of the cylinder 5).
form. The second chamber 72 communicates with the pressure detection tube 25 in the air chamber A (corresponding to the "burner unit 1" side of the present invention) through a second communication pipe 721.

Therefore, the internal pressure of the second chamber 72 is equal to the total pressure (static pressure and dynamic pressure) P in the vicinity of the fan to the air chamber. or,
The first chamber 71 is communicated with the sunrise side of the nozzle 31 through a first communication pipe 711.

Therefore, the internal pressure of the first chamber 71 is equal to the internal pressure P5 on the exit side of the nozzle 31. Note that the effective area of the first diaphragm 61 is equal to the effective area of 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, 75] 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 3474, through the raw gas inlet 741, and after passing through the valve section 9, it enters the fifth chamber 75, and then flows through the outlet 751. It is discharged from the cylindrical body 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.

Next, the installation state of the pressure detection tube 25 will be described in detail based on FIGS. 2 and 3.

In the figure, the pressure detection tube 25 is installed so as to pass through the wall of the blower tube 241. This pressure receiving tube 25 can rotate around its axis (θ in FIG. 3 is a rotation angle).

Reference numeral 251 indicates a pore, which is formed in the side wall of the tip end of the pressure detection tube 25 . The internal pressure (
static pressure and dynamic pressure) are transmitted to the second chamber 72 of the ratio control valve section C. Therefore, if the pressure detection tube 25 is rotated about its axis, the dynamic pressure applied to the pore 251 changes, and as a result, the differential pressure applied to the second diaphragm 62 can be adjusted.

FIG. 4 shows a second embodiment. In this embodiment, the flow velocity distribution in the blast pipe 241 (see the imaginary arrow) is used to move the pressure tube 25 against the wall of the blast pipe 241.
By moving forward and backward (see arrows), the dynamic pressure that the pores 251 receive is adjusted.

FIGS. 5 and 6 show a third embodiment. In this embodiment, the pressure detection tube 25 is fixed to the wall of the blower tube 241, and the baffle plate 26 is rotatably installed on the wall of the blower tube 241. In this embodiment, by rotating the baffle plate 26 (see FIG. 6), the pores 25
This is to adjust the dynamic pressure received by 1.

FIG. 7 shows a fourth embodiment. In this embodiment, the pressure detection tube 25 is fixed to the wall of the blower tube 241, and the baffle plate 27 is installed so as to be movable toward and away from the wall of the blower tube 241 (see arrows). In this example,
By moving the baffle plate 27 back and forth, the dynamic pressure that the pores 251 receive is adjusted.

Therefore, this gas burner device is manufactured as follows.

5 6 When the amount of combustion air increases, the differential pressure on both sides of the burner (P:l
-1) 4) becomes large and pushes out 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 raw gas flows to the hollow part G. The amount increases. Then, 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 the differential pressure between these two (P) increases.

pa) and (P2-P,) are applied in opposing directions via the operating rod 8, so the operating rod 8 is displaced until these loads are balanced, and the differential pressure receiving section 62 on both sides of the burner section and the nozzle on both sides are displaced. The opposing forces of the differential pressure receiving parts 61 and 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/small diaphragm area) (C>1.), and the direction of the load applied to the diaphragm and plate valve. is positive in the upward direction.

(1) Load applied to the first gas-related diaphragm P5S ... ■ Load applied to the third diaphragm P, S ... ■ Load applied to the plate valve P2 S-P, S ... ■ ■＋■＋■ (P2-p,) S ... ■ (2), Load applied to the air-related first diaphragm P3S ... ■ Load applied to the second diaphragm p, cs-p3cs ... ■ 7 8 Third diaphragm The load applied to P4S...■ ■＋■＋■ is (P4-P,) (C-1)S... ■The difference in load between the above ■ and the above ■ becomes the valve opening/closing force, and these are balanced. Displaced up to. Therefore, in the equilibrium state, ■--■, (P2-Ps)/(P,-P4)=C-1, and the ratio of the gas differential pressure to the air differential pressure becomes a constant 01, and as a result, the air Even if the amount is changed, the raw gas amount changes while the air ratio remains constant.

Further, in the present invention, since the dynamic pressure that the pressure receiving pipe 25 receives can be adjusted, the air ratio can be easily adjusted.
It has wide adaptability (versatility) to various gas fuels and various burners.

FIG. 8 shows a fifth embodiment, which can be applied to the previous 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; (1) To adapt the air ratio characteristics to the burner.

〔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 the first diaphragm and the bottom plate at one end of the cylindrical body A first 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 fourth chamber is formed between the valve body 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. raw gas can be introduced into the gas outlet, and the raw gas in the fifth chamber can be supplied to the gas burner section through the gas outlet; The fifth chamber and the inlet side of the nozzle are communicated via a gas supply pipe, and the second chamber and the burner section entry 11 side are communicated via a second communication path, and the The third chamber and the outlet side of the burner section are communicated via a second communication passage, and the effective areas of the first diaphragm, the third diaphragm, and the valve body are made substantially equal, and the effective areas of the second diaphragm are made substantially equal. The effective area is made larger than the effective area of the first diaphragm, the third diaphragm, and the valve body, and further, the total pressure near the fan on the burner inlet side can be detected in the second communicating passage, and the total pressure near the fan on the burner inlet side can be detected. Since the total pressure can be adjusted, the nozzle outlet pressure P
5 can be detected in the first chamber of the ratio control valve section, and the nozzle population pressure P2 can be detected in the fifth chamber, and the differential pressure (P3-P) between the burner section inlet pressure P3 and the burner section outlet pressure 1)4 , ) can be detected in the second and third chambers. Also,
Feed gas pressure can be detected in the fourth chamber.

Therefore, due to the differential pressure (pz-p, ) on both sides of the burner section, the second diaphragm (air differential pressure receiving section) 62 moves 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 gas flowing to the bar portion G increases. Then, the differential pressure between both sides of the nozzle (“nozzle outlet side and nozzle inlet side”, hereinafter referred to as “between”) 1) 2-P,
increases, 1 2 -th diaphragm 61 and plate valve (raw gas differential pressure receiving part)
92 receives 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 P2
PS) applies loads in opposing directions via the operating rod 8, so the operating rod 8 is displaced until these loads are balanced, and the differential pressure receiving portion 62 on both sides of the bar portion, the differential pressure receiving portion 61 on both sides of the nozzle, The opposing forces 92 converge at 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, since the static pressure and dynamic pressure on the burner inlet side can be detected in the second communication passage and the dynamic pressure received can be adjusted, 1. The differential pressure received by the second diaphragm 62 can be easily changed. As a result, the structure can easily adjust the air ratio and has wide adaptability (versatility) to various gas fuels and various banners.

3 4

[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 an enlarged sectional view of the ■ part in Fig. 1, and Fig. 3 is an enlarged sectional view of the
4 is a partial sectional view of the second embodiment; FIG. 5 is a partial sectional view of the third embodiment; FIG. 6 is a sectional view taken along the line ■-■ in FIG. FIG. 7 is a partial sectional view of the fourth embodiment, FIG. 8 is a sectional view of the fifth embodiment, and FIG. 9 is a sectional view of the conventional example. Ratio control valve part Gas burner part Air blowing means (blow fan) Pressure receiver pipe Raw gas supply pipe Raw gas nozzle Cylindrical body Bottom plate Bottom plate First diaphragm Second diaphragm Third diaphragm First chamber First communication pipe (first communication passage) Second chamber Second communication pipe (second communication passage) Third chamber third communication pipe (third communication passage) Fourth chamber gas inlet pipe Fifth chamber gas discharge pipe Operating rod plate valve (valve body) 5 6 Evening diagram VT, Figure 3 Figure 6 [≧(1 Figure 9/4 Procedural amendment (method) 1. Indication of case 1999 Patent Application No. 203593 2,
Name of the invention: Gas burner device 3, relationship with the amended case Patent distributor address: 1370 Kadoya, Hamaoka-cho, Ogasa-gun, Shizuoka Prefecture Name: Aiken Kogyo Co., Ltd. Representative: Kono Sanbe 4, Agent: 430, former Hamamatsu City, Shizuoka Prefecture 295 of Shiromachi 218, date of amendment order: November 28, 1 year 6, subject of amendment: drawing 7, content of amendment (I), engraving of the drawing originally attached to the application (no change in content) . (Delivery date) ・To the attached sheet

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 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 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. The first diaphragm, the third diaphragm, and the valve body are made to have substantially equal effective areas, and the effective area of the second diaphragm is made to be larger than the first diaphragm. , larger than the effective area of the third diaphragm and the valve body, and further, in the second communicating passage, the total pressure near the fan on the burner inlet side can be detected, and the detected total pressure can be adjusted. A gas burner device characterized by: