JP6215594B2 - Comrobana - Google Patents

Description

  The present invention includes a main burner portion having a large number of main flame openings opened on the outer peripheral surface of the burner head, and a sub burner portion having a large number of sub flame openings opened on the outer peripheral surface of the burner head below the main flame opening. It relates to a stove with.

  Conventionally, this type of burner is switched between a state in which fuel gas is supplied only to the sub-burner portion and only the sub-burner portion is burned, and a state in which fuel gas is supplied to the main burner portion and the main burner portion is also burned. What was made freely is known (for example, refer patent document 1).

  Here, in the above-mentioned conventional example, the main burner part and the sub burner part are a natural air supply type in which the primary air is sucked from the inlet of the upstream end of each mixing pipe for the main burner and the sub burner. An air-fuel mixture having an excess air ratio (primary air amount / theoretical air amount) of less than 1 is supplied to the main burner portion and the sub-burner portion via each mixing tube. Further, conventionally, the excess air ratio of the air-fuel mixture supplied to the main burner section is made higher than the excess air ratio of the air-fuel mixture supplied to the sub-burner, and the flame of the main burner section is long in the upward direction for secondary air. There is also known one capable of suppressing the extension (see Patent Document 2).

  By the way, in order to improve the thermal efficiency at the time of heating a cooking container with a stove burner, it is desirable to make a burner outer diameter (outer diameter of a burner head) small so that a cooking container can be heated over the center part of the bottom face. It is. However, if the outer diameter of the burner is reduced, the pressure loss inside the burner increases, and the amount of primary air sucked decreases. Accordingly, in order to prevent a combustion failure due to a shortage of primary air in the main burner portion, the outer diameter of the burner cannot be made very small, and the thermal efficiency has not been improved sufficiently.

JP 2008-281271 A JP 2009-58195 A

  In view of the above, an object of the present invention is to provide a stove burner in which a combustion failure due to a shortage of primary air in the main burner portion does not occur even when the burner outer diameter is small.

In order to solve the above-described problems, the present invention provides a main burner portion having a large number of main flame openings opened on the outer peripheral surface of the burner head, and a plurality of sub-openings opened on the outer peripheral surface of the burner head below the main flame openings. A sub-burner portion having a flame opening, a state in which fuel gas is supplied only to the sub-burner portion and only the sub-burner portion is burned, and a state in which fuel gas is supplied to the main burner portion and the main burner portion is also burned In the stove burner that is freely switchable, the sub-burner section is composed of a natural air supply type burner in which primary air is sucked from the inlet of the upstream end of the sub-burner mixing pipe, and the main burner section is Consists of a forced air supply burner that forcibly supplies primary air from an air supply fan connected to the mixing pipe for the burner. Fuel gas is supplied to the main burner, and fire is transferred from the secondary burner to the main burner. When making the fuel gas to the main burner Starting supply until a predetermined time elapses, and stop the air supply fan, or a characterized to Rukoto lower than the reference speed corresponding to the rotational speed of the air supply fan to the supply amount of fuel gas to the main burner unit To do.

  According to the present invention, since the main burner portion is composed of a forced air supply burner, even if the burner outer diameter is small and the pressure loss is large, combustion failure due to insufficient primary air does not occur. Therefore, it is possible to reduce the outer diameter of the burner and improve the thermal efficiency in a strong fire state in which the main burner portion is also combusted. In addition, if the auxiliary burner unit is also composed of a forced air supply type burner, the amount of fuel gas supplied to the auxiliary burner unit cannot be reduced so as to prevent blow-off. If a natural air supply type burner is used, the amount of fuel gas supplied to the sub-burner can be sufficiently reduced without causing blowout, and a large turndown ratio can be secured.

Also, if there are many primary air quantity at the time of ignition of the main burner unit, but produces a problem such as flashback and ignition noise is large, in the present invention, the air supply fan as stops when the ignition of the main burner unit Or by lowering the fan rotation speed.

The perspective view of the stove burner of embodiment of this invention. Sectional drawing cut | disconnected by the II-II line | wire of FIG. The flowchart which shows the control content of the air supply fan at the time of the supply start of the fuel gas to a main burner part.

  Referring to FIG. 1, a stove burner 1 according to an embodiment of the present invention includes a burner body 2 inserted into a burner opening of a stove top plate (not shown), and an annular burner head 3 on the burner body 2. ing. On the outer peripheral surface of the burner head 3, a large number of main flame outlets 4m and auxiliary flame outlets 4s located therebelow are opened at intervals in the circumferential direction. Note that the total opening area of the auxiliary flame opening 4s is smaller than the total opening area of the main flame opening 4m.

  As shown in FIG. 2, the burner body 2 includes an inner and outer triple cylinder body including an outer cylinder body 21, an intermediate cylinder body 22, and an inner cylinder body 23. The burner head 3 is fitted into an annular lower head member 31 having a cylindrical portion 31a fitted to the intermediate cylindrical body 22 of the burner body 2 on the inner periphery, and an inner cylindrical body 23 of the burner body 2 on the inner peripheral portion of the lower surface. It is comprised with the cyclic | annular upper head member 32 which hung the cylindrical part 32a to join.

  An upper annular wall 33 on which the upper head member 32 is seated is erected on the outer peripheral portion of the upper surface of the lower head member 31. The upper annular wall 33 is formed with a large number of grooves that form a main flame opening 4m that is recessed downward from the upper end surface with a circumferential interval. The upper ends of these grooves are closed by the upper head member 32, so that the main flame opening 4m is defined between the lower head member 31 and the upper head member 32. The main flame opening 4m communicates with a space surrounded by the lower head member 31, the upper head member 32, the intermediate cylinder 22 and the inner cylinder 23 of the burner body 2, and the lower head member 31, the upper head The member 32, the intermediate cylinder 22 and the inner cylinder 23 constitute a main burner portion 1m having a main flame opening 4m.

  Further, a lower annular wall 34 that is seated on the upper end portion of the outer cylinder 21 of the burner body 2 is suspended from the outer peripheral portion of the lower surface of the lower head member 31. The lower annular wall 34 is formed with a large number of grooves serving as the auxiliary flame ports 4s that are recessed upward from the lower end surface thereof with a circumferential interval. Then, the lower end of these grooves is closed by the upper end portion of the outer cylindrical body 21 so that the auxiliary flame opening 4 s is defined between the burner body 2 and the lower head member 31. Further, the auxiliary flame opening 4s communicates with a space surrounded by the lower head member 31, the outer cylinder 21 and the intermediate cylinder 22 of the burner body 2, and these lower head member 31, the outer cylinder 21, and the intermediate cylinder. The body 22 constitutes the auxiliary burner portion 1s having the auxiliary flame opening 4s.

  The burner 1 further includes a main burner mixing tube 5m communicating with a space between the intermediate cylinder 22 and the inner cylinder 23 of the burner body 2, and an outer cylinder 21 and an intermediate cylinder 22 of the burner body 2. And a sub-burner mixing pipe 5 s communicating with the space between them. Referring to FIG. 1, the fuel gas is supplied to the main burner mixing pipe 5m through the main burner gas supply path 6m branched from the common gas supply path 6, and the sub burner mixing pipe 5s is connected to the common burner mixing pipe 5s. Fuel gas is supplied through a sub-burner gas supply path 6 s branched from the gas supply path 6.

  The common gas supply path 6 is provided with an original solenoid valve 61 and a gas flow rate adjusting valve 62, and the main burner gas supply path 6m is provided with a main burner solenoid valve 63. Then, by closing and opening the main burner solenoid valve 63, the fuel gas is supplied only to the sub-burner portion 1s and only the sub-burner portion 1s is combusted, and the fuel gas is also supplied to the main burner portion 1m. Thus, the main burner 1m can also be switched to a state of burning. An ignition plug 7 is provided so as to face one place in the circumferential direction of the sub-burner portion 1s, and the sub-burner portion 1s is subjected to a spark discharge by the ignition plug 7 by an ignition operation of an unillustrated operating member for ignition. Ignited.

  Here, the sub-burner portion 1s has a natural structure in which primary air is sucked from the inflow port 5sa as fuel gas is injected from a gas nozzle (not shown) facing the inflow port 5sa at the upstream end of the sub-burner mixing pipe 5s. Consists of an air supply burner. On the other hand, an air supply fan 8 is connected to the upstream end of the main burner mixing pipe 5m. The main burner portion 1m is configured by a forced air supply burner that forcibly supplies primary air from the air supply fan 8. A gas inlet 5ma connected to a gas nozzle (not shown) inside the mixing pipe 5m is provided on the side surface in the vicinity of the upstream end of the main burner mixing pipe 5m, and the main burner gas supply path is connected to the gas inlet 5ma. 6m is connected.

  The original solenoid valve 61, the gas flow rate adjusting valve 62, the main burner solenoid valve 63, and the air supply fan 8 are controlled by control means (not shown) including a microcomputer. The original electromagnetic valve 61 is controlled to be opened by the ignition operation of the point fire extinguishing operation element and closed by the fire extinguishing operation. The gas flow rate adjusting valve 62 is controlled so that the opening degree is changed in conjunction with a thermal power adjusting operator (not shown). The main burner solenoid valve 63 is controlled so as to be opened when the heating power adjusting operator is operated to the high fire side beyond a predetermined intermediate position. Further, the supply fan 8 supplies the fuel gas to the main burner 1m when the thermal power adjusting operation element is operated to the high fire side beyond the intermediate position, that is, when the combustion is performed in the main burner 1m. It is controlled to rotate at a reference rotational speed corresponding to. This reference rotational speed is set so that the excess air ratio of the air-fuel mixture supplied to the main burner portion 1m becomes a relatively high value of about 0.8 to 1.

  If the main burner portion 1m is configured with a forced air supply burner as in this embodiment, even if the burner outer diameter is small and the pressure loss is large, combustion failure due to insufficient primary air does not occur. Accordingly, it is possible to reduce the outer diameter of the burner and improve the thermal efficiency in a high fire state where the main burner portion 1m is also burned. If the sub-burner unit 1s is also composed of a forced air supply type burner, the amount of fuel gas supplied to the sub-burner unit 1s cannot be reduced so as to prevent blow-off. If the burner unit 1s is composed of a naturally supplied burner, the amount of fuel gas supplied to the sub-burner unit 1s can be sufficiently reduced without fear of blow-off, and a large turndown ratio can be secured. .

  By the way, when the main burner solenoid valve 63 is opened, fuel gas is supplied to the main burner portion 1m, and the primary burner portion 1m is supplied to the main burner portion 1m when the sub burner portion 1s is transferred to the main burner portion 1m and ignited. If the amount of air is large, problems such as flashback and increased ignition noise occur. Further, when the main burner solenoid valve 63 is initially opened, the flow of the gas that has passed through the gas flow rate adjustment valve 62 to the main burner gas supply path 6s is started, and the amount of fuel gas supplied to the sub burner unit 1s is started. Therefore, if the amount of primary air supplied to the main burner portion 1m is large, air blown out from the main burner portion 1m may cause blowout in the sub burner portion 1s.

  Therefore, in this embodiment, the air supply fan 8 is controlled as follows by the control means. That is, as shown in FIG. 3, when the supply of the fuel gas to the main burner portion 1m is started, that is, when the main burner electromagnetic valve 63 is opened (STEP 1), the air supply fan 8 is switched to the main burner electromagnetic. The valve 63 is maintained in a stopped state as before the valve 63 is opened, or the air supply fan 8 is rotated at a rotation speed lower than a reference rotation speed corresponding to the amount of fuel gas supplied to the main burner 1m (STEP2 ). Then, it is determined whether or not a predetermined time (for example, 2 seconds) has elapsed from the opening of the main burner solenoid valve 63 (supply of fuel gas to the main burner portion 1m) (STEP 3), and until the predetermined time has elapsed. The air supply fan 8 is maintained in a stopped state or a low rotation state, and after a predetermined time has elapsed, the air supply fan 8 is rotated at a reference rotational speed corresponding to the amount of fuel gas supplied to the main burner portion 1m (STEP 4).

  As a result, when supplying fuel gas to the main burner unit 1m to ignite the main burner unit 1m, problems such as backfire, loud ignition noise, and blowout of the sub burner unit 1s are prevented. can do.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to this. For example, in the above embodiment, the gas flow rate adjusting valve 62 is provided in the common gas supply path 6, but the gas flow rate adjusting valve is provided in each of the main burner gas supply path 6m and the sub burner gas supply path 6s. You may set up. In this case, the main-burner solenoid valve 63 of the above-described embodiment is provided with the gas flow rate adjusting valve interposed in the main-burner gas supply path 6m having a valve closing function for completely closing the main-burner gas supply path 6m. It can be omitted.

  DESCRIPTION OF SYMBOLS 1 ... Combustor, 1m ... Main burner part, 1s ... Sub burner part, 3 ... Burner head, 4m ... Main flame opening, 4s ... Secondary flame opening, 5m ... Main burner mixing pipe, 5s ... Sub burner mixing pipe, 8 ... Air supply fan.

Claims (1)

A main burner portion having a number of main flame openings opening on the outer peripheral surface of the burner head, and a sub-burner portion having a number of sub flame openings opening on the outer peripheral surface of the burner head below the main flame opening, In a stove burner that can be switched between a state in which fuel gas is supplied only to the burner portion and only the sub-burner portion is burned and a state in which fuel gas is supplied to the main burner portion and the main burner portion is also burned,
The sub-burner section is composed of a natural air supply type burner in which primary air is sucked from the inlet of the upstream end of the sub-burner mixing pipe,
The main burner section is composed of a forced air supply burner that forcibly supplies primary air from an air supply fan connected to the main burner mixing tube ,
When supplying fuel gas to the main burner part and firing and igniting from the sub burner part to the main burner part, the air supply fan is stopped until a predetermined time has elapsed from the start of supply of fuel gas to the main burner part, Alternatively, stove burners, wherein to Rukoto lower than the reference speed corresponding to the rotational speed of the air supply fan to the supply amount of the fuel gas to the main burner unit.

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