JP5794844B2 - Turbulence generator in gas stove - Google Patents

Description

  The present invention relates to a gas nozzle provided with a gas jet nozzle hole, a gas flow path for supplying a combustion gas to the nozzle hole, a fuel gas jetted from the gas nozzle, and an ejector effect caused by jetting the fuel gas. A gas combustion section having a mixing section for mixing the combustion air and a flame forming section for burning the air-fuel mixture mixed in the mixing section, and a fuel gas in the gas flow path of the gas nozzle The present invention relates to a turbulent flow forming method in a gas stove provided with a turbulent flow forming body that causes turbulence in the flow of the gas, and a turbulent flow forming device in the gas stove.

  The gas stove sucks the primary air for combustion as combustion air by the ejector effect caused by the ejection of the fuel gas from the gas nozzle, and mixes the fuel gas ejected from the gas nozzle and the suctioned primary air for combustion in the mixing section The air-fuel mixture is generated and guided to the flame forming section. The flame forming section supplies the secondary air for combustion while performing the primary combustion of the air-fuel mixture to perform the secondary combustion. It burns.

Further, the gas stove is provided with a turbulent flow forming body that causes a turbulence in the flow of the fuel gas in the gas flow path in the gas nozzle, and even if the ejection speed of the fuel gas ejected from the gas nozzle is reduced, the turbulent flow is formed. By the body, it is possible to prevent the combustion air suction ratio (hereinafter referred to as air suction ratio) from being lowered and to form a favorable air-fuel mixture.
In order to provide a turbulent flow forming body that disturbs the flow of fuel gas in the gas flow path of the gas nozzle in this way, conventionally, a gas flow ejected from the nozzle is arranged by placing a cap as an obstacle upstream of the nozzle hole. A technique is known that promotes the suction of primary air by a gas flow in a mixing tube portion of a burner by making a turbulent flow state. (For example, refer to Patent Document 1.) In the above-described prior art, even when the gas amount suddenly decreases when the user throttles the gas amount, the turbulent flow state is maintained to suppress the decrease in the air suction ratio. It is.

  Further, the fuel gas is ejected from the ejection hole provided in the gas burner and provided in the inner space of the cylinder, and with the ejection of the fuel gas, the suction of the cylinder from the suction hole provided on the outer periphery of the cylinder is performed. A technique is known that can improve the primary air rate by using a gas nozzle that joins the primary air sucked into the inner space with the fuel gas and jets it from the opening provided at the tip of the cylinder toward the gas burner. Yes. (For example, see Patent Document 2.)

JP-A-11-211028 Japanese Patent Laid-Open No. 11-182819

  As shown in FIG. 7, when the technique of Patent Document 1 and the technique of Patent Document 2 are used in combination, the primary air suction ratio (hereinafter referred to as the primary suction rate) when the gas flow rate is small can be further increased. Even if the amount of gas suddenly drops due to an instrument plug operation, etc., the effect of maintaining the turbulent flow state and suppressing the decrease in suction can be obtained. However, there are the following problems, and improvement of these points is desired. It was.

  (1) Since the obstacle in the nozzle is charged in the nozzle, it is difficult to determine whether the nozzle is present or not from the appearance of the nozzle, and it is difficult to check when it is left out. (Although it is possible by inspection such as passing a pin gauge through the nozzle hole, it will take time.)

  In other words, when producing products and parts using this technology in the factory, inspection cannot be performed by appearance, so inspection by an inspection device such as a pin gauge is required, resulting in an increase in inspection man-hours. Therefore, improvement has been desired.

  (2) Since turbulence is added to the gas flow, only turbulence corresponding to the gas ejection speed (gas flow rate) can be added.

  However, when the type of fuel gas or the amount of gas combustion is different, the gas ejection speed (gas flow rate) is different and the combustion state may become unstable.

  In other words, as a gas stove, a large-power gas combustion unit that forms a large-diameter flame corresponding to a large heated object such as a large-diameter cooking pan or a small-diameter flame-forming unit. There is a gas stove equipped with a gas combustion section for small thermal power that forms a small-diameter flame corresponding to a small object to be heated such as a cooking pan, and the maximum in the gas combustion section for large thermal power The gas flow amount is larger than the maximum gas flow amount in the gas combustion section for small thermal power.

  In the case of a turbulent flow generator that causes turbulence depending on the gas ejection speed (gas flow rate) for a gas stove including gas combustion sections having different maximum gas flow rates, the maximum gas flow rate is different. However, there is a case where an appropriate mixed gas cannot be generated, and an improvement has been desired.

  Also, as the fuel gas used in the gas stove, different types of fuel gas, such as LP gas and city gas, may be used. However, different types of fuel gas have a calorific value per unit gas amount. The fuel gas with a large calorific value needs to increase the ejection speed from the gas nozzle to enhance the ejector effect than the fuel gas with a small calorific value. When a flow forming body is used, an appropriate mixed gas may not be generated due to the difference in the turbulent flow effect between the fuel gas with a large calorific value and the fuel gas with a small calorific value, and an improvement is desired. It was.

  The object of the present invention is that it is possible to easily check the presence or absence of mounting during production, and to generate an appropriate mixed gas even when the maximum gas flow amount in the gas combustion section is different. The object is to provide a turbulent flow formation method in a gas stove that enables combustion.

A turbulent flow forming device in a gas stove according to the present invention is:
The main body is composed of a nozzle hole for gas ejection, a gas nozzle having a gas flow path for supplying fuel gas to the nozzle hole, and a cylinder having a suction port, and the fuel gas is ejected from the nozzle hole. Due to the ejector effect of the above, the combustion air is sucked from the suction port as primary primary air, and the fuel gas ejected from the nozzle hole and the primary primary air are mixed in the cylinder to form the first air-fuel mixture. Further, the first air-fuel mixture is ejected from the front end of the cylinder, the first air-fuel mixture is supplied, and the first air-fuel mixture is sucked by an ejector effect caused by being ejected from the front end of the cylinder. A gas combustion unit comprising: a mixing unit that mixes combustion air and the first air-fuel mixture to form a second air-fuel mixture; and a flame combustion unit that burns the second air-fuel mixture A turbulent flow forming device, the first characteristic configuration in,
The cylindrical body is provided with a turbulent flow forming body that causes a turbulence in the flow of the first air-fuel mixture ejected from the tip of the cylindrical body, and the turbulent flow forming body has a central axis of the nozzle hole. The turbulence forming body is disposed on an extended extension shaft, and the turbulent flow forming body is constituted by three or more radial bodies extending from the extension shaft toward the cylindrical body .

  That is, in the first characteristic configuration of the present invention, the cylindrical body is provided with a turbulent flow forming body that causes turbulence in the flow of the first air-fuel mixture ejected from the tip of the cylindrical body.

  In other words, as a gas stove, a large-scale gas combustion section that forms a large-diameter flame corresponding to a large-scale object to be heated, such as a large-diameter cooking pan, or a small-scale heating such as a small-diameter cooking pan Equipped with a plurality of types of gas combustion parts so that a combustion state corresponding to the difference in the size of the object to be heated can be obtained, such as a gas stove with a gas combustion part for small heating power that forms a small-diameter flame corresponding to an object Although there is a gas stove, the gas combustion part for large thermal power has a large maximum gas flow rate, and the gas combustion part for small thermal power has less maximum gas flow rate than the gas combustion part for large thermal power. And the above-mentioned plural types of gas combustion sections have different maximum gas flow amounts. In addition, even when there is a difference in the maximum gas flow rate in such a gas combustion section, Reynolds related to the flow of the air-fuel mixture so that a turbulent flow forming effect can be produced in a wide range of gas flow rates. The cylindrical body is provided with a turbulent flow forming body that generates a turbulence in the flow of the first air-fuel mixture that is ejected from the inside of the cylindrical body so that the number becomes a large value.

  More specifically, the flow rate of the first air-fuel mixture flowing out from the opening provided at the tip of the cylindrical body is the sum of the flow rate of the primary air sucked from the suction port and the flow rate of the gas flowing through the nozzle hole. Therefore, the value is larger than the flow rate of the gas flowing through the gas nozzle, and even if a small turbulence forming body is used, the effect of causing a large turbulence can be obtained.

  That is, when the gas flow amount passing through an arbitrary flow path changes from a large value to a small value, a turbulent flow with a large Reynolds number is formed when the gas flow amount is a large value. However, when the gas flow rate becomes a value smaller than a certain critical flow rate, the Reynolds number becomes a small value, and a laminar flow is formed instead of a turbulent flow.

  On the other hand, when gas is ejected toward the mixing section of the combustion section in the combustion section and the combustion air is sucked by the ejector effect of this ejection, the gas ejected when the gas to be ejected is turbulent Ejector effect is greater than when laminar flow.

Therefore, when the thermal power is large thermal power, a large ejector effect can be obtained, so that even when good combustion air can be sucked and good combustion is possible, the gas flow rate is reduced when the thermal power is reduced to small thermal power. When the value becomes smaller than a certain limit flow rate, the Reynolds number becomes small and a laminar flow is formed, and the ejector effect is greatly reduced, making it impossible to suck in appropriate combustion air. It can be considered.

On the other hand, by providing the turbulent flow forming body, the gas flow to be ejected can be maintained in the turbulent flow shaped body by the turbulent flow forming body. By providing the cylindrical body instead of the inside, the gas flow in a state where the Reynolds number is large is kept in a turbulent flow body by a turbulent flow forming body. By the small turbulent flow forming body having the passage resistance, an effect of keeping the gas ejection in the burner, that is, the mixing part of the gas combustion part, in the turbulent flow form can be obtained.

  Therefore, according to the first characteristic configuration of the present invention, even when the maximum gas flow amount in the gas combustion section is different, the disturbance in the gas stove that can generate an appropriate mixed gas and perform good combustion is possible. A flow forming body can be provided.

Further , when the turbulent flow forming body is not on an extended axis extending from the central axis of the nozzle hole, it is difficult to cause turbulent flow with respect to the flow of the first air-fuel mixture. Since the forming body is disposed on the extension shaft extending from the central axis of the nozzle hole, a large turbulent flow is generated even with a small passage resistance.

That is, the passing resistance before Kiran flow forming member as much as possible a small passage resistance, can be allowed to rise to high turbulence.

Further , since the turbulent flow forming body is constituted by three or more radial bodies extending from the extension shaft toward the cylindrical body, the first air-fuel mixture passing through the cylindrical body is formed in the cylindrical body. Even when the flow is somewhat biased inside, the turbulence forming body tends to generate turbulence with respect to the flow of the first air-fuel mixture, so that the variation in the effect of generating turbulence is small. can do.

Therefore, even when the first air-fuel mixture passing through the pre-Symbol cylindrical member flows somewhat biased in the interior of the cylindrical body, to be smaller the variation in effect allowed to turbulence by the turbulent flow forming member Can

The second characteristic configuration of the present invention, in addition to the first feature configuration, the turbulent flow forming member is in that provided at the tip of the cylindrical body.

  That is, since the turbulent flow forming body is provided at the tip of the cylindrical body, the presence or absence of the turbulent flow forming body can be determined from the appearance, and it is easy to check whether the turbulent flow forming body is attached or not. It becomes.

Therefore, according to the second characterizing feature of the present invention, in addition to the advantageous effects according to the first feature configuration, the presence or absence of the mounting of the turbulent flow forming member is assumed easily confirmed.

According to a third feature configuration of the present invention, in addition to either the first feature configuration or the second feature configuration, the downstream side of the flow of the first air-fuel mixture as the turbulent flow forming body moves away from the wall surface of the cylindrical body. It is in the point provided curved in the form located in.

  That is, the turbulent flow over a long distance in the flow direction of the first air-fuel mixture in the vicinity of the wall surface of the tubular body where the flow velocity of the first air-fuel mixture flowing around the place where the turbulent flow forming body is mounted in the cylinder is small. In the vicinity of the central axis of the cylindrical body where the formed body is present and the flow velocity of the first mixed gas in the radial direction of the cylindrical body is large, the turbulent flow is formed over a short distance in the flow direction of the first mixed gas. In this way, it can be easily configured to effectively generate turbulent flow according to the distribution of the flow velocity of the first air-fuel mixture in the radial direction of the cylindrical body.

Therefore, according to the third feature configuration of the present invention, in addition to the function and effect of either the first feature configuration or the second feature configuration, according to the flow velocity distribution of the first air-fuel mixture in the radial direction of the cylindrical body. Thus, a turbulent flow forming body that can effectively generate turbulent flow can be easily configured.

According to a fourth characteristic configuration of the present invention, in addition to the third characteristic configuration, the turbulent flow forming body is provided so as to protrude from the tip of the cylindrical body to the downstream side of the flow of the first air-fuel mixture. .

  That is, since the turbulent flow forming body is provided so as to protrude downstream of the flow of the first air-fuel mixture from the tip of the cylindrical body, the turbulent flow forming body on the extension shaft is provided in the cylindrical body. Therefore, the turbulent flow can be generated with a smaller passage resistance.

Therefore, according to the fourth characteristic configuration of the present invention, in addition to the function and effect of the third characteristic configuration, it is possible to generate turbulent flow with a smaller passage resistance.

Top view of gas stove Perspective view of the stove Longitudinal cross section of the stove Vertical section of a two-stage gas nozzle with a turbulent flow forming body Perspective view of a two-stage gas nozzle with a turbulence generator Perspective view of a two-stage gas nozzle with a turbulence generator Perspective view of a two-stage gas nozzle with a turbulence generator Longitudinal section of a two-stage gas nozzle with turbulence generator showing the relationship with the flow velocity Sectional view showing the prior art

Hereinafter, an embodiment of a turbulent flow forming device in a gas stove according to the present invention will be described with reference to the drawings.
As shown in FIG. 1, the gas stove includes a three-burner burner 1 as a gas combustion unit and a grill (not shown), and is configured as a built-in type gas stove.
The three stove burners 1 are constituted by a large thermal power burner 1a, a standard burner 1b, and a small thermal power burner 1c.
Hereinafter, the stove burner 1 will be described. Since the large thermal power burner 1a, the standard burner 1b, and the small thermal power burner 1c have basically the same structure, the configuration of the stove burner 1 will be described with the large thermal power burner 1a as a representative. If necessary, the standard burner 1b and the small fired burner 1c will also be described.

  As shown in FIGS. 2 and 3, the stove burner 1 has a burner cap 3 detachably mounted on the burner body 2 and is exposed on the top plate 4 from the through hole 5 of the top plate 4. . An annular burner ring 6 is interposed between the burner body 2 and the through hole 5 of the top plate 4, and between the burner ring 6 and the top plate 4 and between the burner body 2 and the burner ring 6. The space is fixed with a watertight structure through a packing, and prevents the broth or the like from falling down from the top 4.

  Further, the virtues 7 are placed on the top plate 4 so as to surround the through holes 5. Gotoku 7 has an annular leg 7a to be placed on the top plate 4 and a plurality of U-shapes on which a cooking utensil such as a pan is placed by projecting upward and centrally from an arbitrary position of the leg 7a. The claw portion 7b is configured so that the locking portion provided on the leg portion 7a is locked to the locked portion of the burner ring 6 attached to the top plate 4 or the like in a circumferentially stopped state. It is placed on the top 4. Further, in the standard burner 1b instead of the large thermal power burner 1a described above, an opening is formed in the burner cover 8 described later, and the pan bottom temperature sensor S is placed facing upward through the opening. The pan bottom temperature sensor S detects the temperature of the pan bottom when the pan is installed on the stove burner 1, and various controls of the combustion of the stove burner 1 can be performed according to the detected temperature. Note that the pan bottom temperature sensor S may be provided to all the stove burners 1.

As shown in FIG. 2, the burner body 2 is configured in a substantially annular shape, and an annular burner cap 3 is placed on the burner body 2, and the burner cap 3 is similar to the burner body 2 such as the ADC 12. The outer diameter of the aluminum die-cast product is about 60 mm, and the outer diameter of the burner body 2 and the burner cap 3 of the standard burner 1b is about 60 mm, similar to the large thermal burner 1a. Is smaller than this.

  As shown in FIGS. 2 and 3, the burner body 2 integrally has a mixing tube 9 as a mixing portion, and the burner body 2 and the mixing tube 9 (mixing portion) are formed by aluminum die casting such as ADC 12. It is a product. A two-stage gas nozzle 10N with a turbulent flow forming body that discharges a first air-fuel mixture, which will be described later, is supported by a support plate 9a mounted so as to cover the gas inlet side opening of the mixing tube 9 (mixing unit). Is provided. An air intake port 9b is formed in the support plate 9a at an appropriate interval in the circumferential direction. From the two-stage gas nozzle 10N with a turbulent flow forming body, which will be described later, a first air-fuel mixture (fuel gas and front primary air (which will be described later) When the air-fuel mixture with the combustion air) is ejected, the combustion air is sucked from the air intake port 9b due to the ejector effect caused by ejecting the first air-fuel mixture, and the first air is mixed in the mixing pipe 9 (mixing portion). The mixed gas and the combustion air are mixed to generate a mixed gas (second mixed gas). The burner body 2 is formed in an annular shape, and secondary air for combustion is supplied even through a space (upper and lower openings 12 described later) on the inner peripheral side of the burner body 2. The two-stage gas nozzle 10N with a turbulent flow forming body will be described in detail later.

  The burner body 2 is provided with an annular gas supply chamber 11, which is in communication with a mixing tube 9 (mixing unit). As shown in FIG. 2 and FIG. 3, the gas supply chamber 11 is disposed so as to overlap with an inner cylinder portion 13 that forms an upper and lower opening 12 inside and a radially outward direction of the inner cylinder portion 13 at a predetermined interval. It is an annular space portion that opens upward and is surrounded by the outer cylindrical portion 14 and the lower surface portion 15 that connects the lower ends of the inner cylindrical portion 13 and the outer cylindrical portion 14. An inclined surface is formed on the lower surface portion 15 of the gas supply chamber 11 so as to be gradually positioned upward from the end portion on the side where the mixing pipe 9 (mixing portion) is connected to the opposite end portion. That is, the upper and lower openings 12 of the burner body 2 are formed so as to open not only downward but also to the side in the lower part.

  As shown in FIGS. 2 and 3, the burner cap 3 is an annular block body having an upper and lower opening 12 that is opened up and down in the center, and the outer peripheral portion of the lower surface of the burner cap 3 is mounted on the burner body 2. Thus, the gas supply chamber 11 is formed. That is, the burner body 2 has an annular shape composed of a cylindrical inner tube portion 13 and an outer tube portion 14, and the outer peripheral portion of the burner cap 3 is placed on the burner body 2, whereby the inner tube portion 13 and the outer tube are placed. The upper part between the parts 14 is closed to form the gas supply chamber 11.

In the portion of the lower surface of the burner cap 3 placed on the burner body 2, a plurality of flame opening grooves 16 are formed radially in the circumferential direction, and when the burner cap 3 is placed on the burner body 2, The outer atmosphere and the inner gas supply chamber 11 communicate with each other through the groove 16, and the mixed gas in the gas supply chamber 11 flows outward through the flame opening groove 16. Therefore, the opening outside the groove 16 for the flame opening constitutes the flame mouth 17 as a flame forming part where the mixed gas burns.
Also, a burner cover 8 is installed on the upper surface of the burner cap 3 to prevent the soup from adhering to the burner cap 3, and the burner body 2 detects an ignition plug 20 that performs an ignition operation and an ignition state. A thermocouple 21 is also provided.

As shown in FIG. 3, the gas nozzle 10 is connected to a gas supply pipe 41 supported in a fixed position by tightening a screw, and a fuel gas supply path 22 for supplying fuel gas to the gas supply pipe 41 is provided in the fuel gas supply path 22. A gas amount adjusting valve 23 that can change and adjust the supply amount of the fuel gas based on the operation of the operator is provided, and the heating power in the stove burner can be changed and adjusted.
Further, the large thermal power burner 1a, the standard burner 1b, and the small thermal power burner 1c are different from each other in the maximum gas flow rate of the fuel gas when adjusted to the maximum thermal power. The maximum gas flow rate is set so that the burner 1a is the largest, the standard burner 1b is smaller than the maximum gas flow rate of the large thermal burner 1a, and the small thermal burner 1c is smaller than the maximum gas flow rate of the standard burner 1b. The maximum gas flow is set. Further, the gas flow amount when adjusted to the minimum thermal power is also set in the order of large thermal power burner 1a> standard burner 1b> small thermal power burner 1c. Incidentally, in this gas stove, city gas (13A) is used as fuel gas.

Hereinafter, the two-stage gas nozzle 10N with a turbulent flow forming body, which will be described with reference to the embodiments, has the following characteristics, and a specific configuration will be described below.

  As shown in FIG. 3, a cylindrical body T is provided on the downstream side of the flow of the fuel gas ejected from the ejection hole (nozzle hole 24) of the gas nozzle 10 to constitute a two-stage gas nozzle 10N with a turbulent flow forming body. .

As shown in FIG. 4, the two-stage gas nozzle 10N with a turbulent flow forming body ejects fuel gas from an ejection hole (nozzle hole 24) of the gas nozzle 10 provided on the inlet side of the cylinder T, and the fuel Air sucked into the internal space of the cylinder T from the suction port K provided on the outer periphery of the cylinder T provided on the downstream side of the injection hole (nozzle hole 24) of the gas nozzle 10 due to the ejector effect accompanying the gas injection ( Called the primary air in the previous stage)
It has a basic structure as a two-stage nozzle that merges with the fuel gas and jets from a jet opening F provided at the tip of the cylinder T toward the gas burner. 4 shows a case where the nozzle 10 is integrally formed with the two-stage gas nozzle 10N with a turbulent flow forming body, but the nozzle 10 is replaced with a two-stage gas nozzle with a turbulent flow forming body as shown in FIG. You may comprise so that isolation | separation from the cylinder T which is a 10N main structural part is possible.

  Further, in the vicinity of the ejection opening F provided at the tip of the cylindrical body T, a turbulent flow that causes a turbulence in the flow of the first air-fuel mixture, which is an air-fuel mixture in which the gas from the gas nozzle 10 and the primary air in the previous stage are mixed. The forming body 26 is provided in the shape of a single character having a width of 0.8 mm in the diameter direction of the ejection opening F. (See FIGS. 4 and 5A.)

  Since the turbulent flow forming body 26 is located on an extended axis extending from the central axis of the nozzle hole 24, a large turbulent flow is generated with a small passage resistance. On the other hand, when the turbulent flow forming body 26 is not on the extended axis obtained by extending the central axis of the nozzle hole 24, the effect of generating turbulent flow is reduced as compared with the case where the turbulent flow forming body 26 is positioned on the extended axis. This has been confirmed by testing.

  In addition, when the turbulent flow forming body 26 that causes the turbulence in the flow of the first air-fuel mixture is provided in the vicinity of the ejection opening F provided at the tip of the cylindrical portion T, the conventional combination technique shown in FIG. As described above, there are the following advantages compared with the case where the obstacle in the nozzle is incorporated in the gas nozzle.

  As shown in FIG. 4, when the flow rate of the gas flowing through the gas nozzle 10 is Q1, and the flow rate of the upstream primary air sucked from the suction port K is Q2, the air-fuel mixture flowing out from the opening provided at the tip of the cylinder T Since the flow rate Q3 of Q3 is Q3 = Q1 + Q2, since Q3 is larger than Q1, an effect of causing a large turbulence by the smaller turbulence generator 26 is obtained. That is, the obstacle in the gas nozzle in the combination of the prior art shown in FIG. 7 causes the gas flow rate Q1 to be disturbed, but in this embodiment, the turbulent flow forming body 26 is changed to the flow rate Q3 of the first air-fuel mixture. Since the Reynolds number at the same gas flow rate is larger in the cylinder T than in the gas nozzle 10, the flow is disturbed by adding a smaller turbulence element (= smaller passage resistance). It can be kept flowing.

  As a result, the reduction in the air suction ratio when the stove's heating power is suddenly reduced from a large fire to a small fire (at the time of sudden expansion) becomes gradual, resulting from a reduction in the combustion speed due to the decrease in the air suction ratio during sudden expansion This makes it difficult for blowout to occur, and the combustion performance when the thermal power is rapidly reduced is further improved.

  Furthermore, (1) it is easy to detect forgetting to insert (it can be seen whether the turbulent flow formation body 26 is present or not), and (2) the gas flow resistance in the gas nozzle 10 can be reduced, so that the gas flow rate (input ) Can be reduced, and the turbulence generator 26 can be shared in a wide range of gas flow rates, and production can be rationalized. (3) The turbulence generator is not a structure in which an obstacle is housed in the gas nozzle 10. Since the structure in which the turbulent flow forming body 26 is attached to the vicinity of the tip of the cylindrical body T of the attached two-stage gas nozzle 10N can be assembled, there are advantages such as easy assembly.

[Another embodiment]
Other embodiments are listed below.

(1) The turbulent flow forming body 26 is in the shape of an arrow wheel having three blades having a width of 0.2 mm in the radial direction from three points at intervals of 120 degrees on the outer periphery of the opening toward the center of the opening, that is, the nozzle hole Although provided in composed form by the cylindrical body 3 or more radial members extending towards the wall of the T from the extension shaft formed by extending the central axis 24, (see FIG. 5B.) above mentioned feathers (radial member) The turbulent flow forming body 26 may be configured to include four or more.

  With this configuration, when the first gas mixture, which is a mixture of gas and air that passes through the ejection opening F, flows somewhat unevenly in the cylindrical body T of the two-stage gas nozzle 10N with a turbulent flow forming body. In addition, the variation in the effect of causing turbulent flow can be reduced.

  (2) As the turbulent flow forming body 26 moves away from the wall surface of the cylindrical body T constituting the vicinity of the ejection portion of the two-stage gas nozzle 10N with the turbulent flow forming body to the central side in the radial direction of the cylindrical body T, The turbulent flow forming body 26 is attached in a curved shape so as to be positioned, and is downstream in the direction in which the gas-air mixture passing through the ejection opening F flows on the distal end side of the ejection opening F. You may comprise so that it may prepare in the shape of a curved arch which protrudes on the circular arc toward the side. (See FIG. 5C.) In this case, the turbulent flow forming body 26 on the central axis may be configured to be located in the open space downstream from the tip of the cylindrical body T.

  By comprising in this way, in the vicinity of the wall surface of the cylinder T in which the flow velocity of the first air-fuel mixture is small in the radial direction of the cylinder T constituting the vicinity of the ejection part of the two-stage gas nozzle 10N with a turbulent flow forming body, In the vicinity of the central axis of the cylindrical body T where the turbulent flow forming body 26 exists over a long distance in the flow direction of the first mixed gas and the flow velocity of the first mixed gas in the radial direction of the cylindrical body T is large. The turbulent flow formation body 26 exists over a short distance in the flow direction of the first air-fuel mixture, but this makes it effective according to the flow velocity distribution of the first air-fuel mixture in the radial direction of the cylinder T. Can cause turbulence. Further, the turbulent flow forming body 26 is provided so as to protrude downstream from the tip of the cylindrical body T, and the turbulent flow forming body 26 on the extension shaft is provided on the cylindrical body T. By being located in the open space downstream of the tip, it becomes possible to generate a large turbulent flow with a smaller passage resistance. (See Figure 6.)

  (3) In the above-described embodiment, the stove burner 1 as a gas combustion unit has been described, but it can also be used in a grill as a gas combustion unit.

  In addition, the numerical value described about the two-stage gas nozzle 10N with a turbulent flow forming body 10N and the turbulent flow forming body 26 shown in the above embodiment is an example, and the present invention is not limited to these numerical values.

9 Mixing section (mixing tube)
DESCRIPTION OF SYMBOLS 10 Gas nozzle 10N Two-stage type gas nozzle with a turbulent flow formation body 17 Flame formation part 24 Nozzle hole 26 Turbulent flow formation body F Ejection opening K Suction port T Cylindrical body

Claims (4)

The main body is composed of a nozzle hole for gas ejection, a gas nozzle having a gas flow path for supplying fuel gas to the nozzle hole, and a cylinder having a suction port,
By ejecting the fuel gas from the nozzle hole, the combustion air is sucked from the suction port as primary air in the previous stage,
The fuel gas ejected from the nozzle hole and the primary air in the previous stage are mixed in the cylinder to form a first mixture, and further, the first mixture is ejected from the tip of the cylinder,
The first air-fuel mixture is supplied, and the first air-fuel mixture is mixed with the combustion air sucked by the ejector effect generated by ejecting the first air-fuel mixture from the tip of the cylindrical body. In a gas stove provided with a gas combustion part having a mixing part for making a gas and a flame forming part for burning the second air-fuel mixture,
The turbulent flow forming device is provided with a turbulent flow forming body that causes turbulence in the flow of the first air-fuel mixture ejected from the tip of the cylindrical body , the turbulent flow forming body, A gas stove that is disposed on an extension shaft extending from the central axis of the nozzle hole, and in which the turbulent flow forming body is constituted by three or more radial bodies extending from the extension shaft toward the cylindrical body. turbulent flow forming device in.   The turbulent flow forming apparatus in a gas stove according to claim 1, wherein the turbulent flow forming body is provided at a tip of the cylindrical body.   The turbulent flow formation in the gas stove according to claim 1 or 2, wherein the turbulent flow forming body is provided so as to be curved in such a manner that the turbulent flow forming body is positioned on the downstream side of the flow of the first air-fuel mixture as the distance from the wall surface of the cylindrical body increases. apparatus.   The turbulent flow forming device in a gas stove according to claim 3, wherein the turbulent flow forming body is provided so as to protrude downstream from the tip of the cylindrical body in the flow of the first air-fuel mixture.