JP3442256B2 - Vaporized oil combustion equipment - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gasification type petroleum combustion apparatus equipped with a heating heater which constitutes a combustion section of a heater or a water heater.

[0002]

2. Description of the Related Art Conventionally, in this type, as disclosed in, for example, Japanese Unexamined Patent Publication No. Hei 8-21606,
In the Lo combustion range, the damper closes the air passage to lower the lower limit value of the combustion air amount while increasing the blow pressure, and as a result, the combustion variable range can be widened. there were.

[0003]

However, in this prior art, if the amount of combustion air is changed while the damper is being driven, the combustion balance will be greatly disrupted. Therefore, the amount of combustion air should be kept constant while the damper is being driven. However, in the opening direction of the damper, there is a problem that the flame blows off because the amount of combustion air increases due to the opening of the damper, and conversely, in the closing direction, the damper is closed. Since the amount of combustion air decreases, there is a problem that soot is generated.

[0004]

The present invention focuses on this point and solves the above-mentioned drawbacks. In particular, the structure of the vaporizer includes a heating heater and a vaporizer for vaporizing fuel oil, and the vaporizer burns the fuel oil. Blower for supplying primary air for the burner and secondary air for the burner section, a blower path for communicating the blower port of the blower with the carburetor and the burner section, and a vaporizer communicating with the blower path A guide passage for guiding the primary air is provided at the jet outlet of the vessel, and a damper for controlling the cross-sectional area of the blower passage at two positions of opening and closing is provided on the windward side of the guide passage, and the drive of the damper is started. At times, the rotation speed of the blower is corrected to a predetermined rotation speed on the rising side in the closing direction and to a predetermined rotation speed on the falling side in the opening direction, and this rotation speed is continued until the damper driving is completed.

[0005]

When the Hi combustion range A in the open state of the damper 52 is switched to the Lo combustion range B in the closed state of the damper 52, the rotation speed of the blower 48 is decreased by closing the damper 52 at the same time when the driving of the damper 52 is started. The rotation speed is raised to a predetermined rotation speed corresponding to the amount, and this rotation speed is maintained while the damper 52 is being driven, and the supply amount of the flow rate pump 58 is also constant.

On the contrary, the Lo combustion range B when the damper 52 is closed
When the damper 52 is switched to the Hi combustion range A in which the damper 52 is open, the rotation speed of the blower 48 is reduced to a predetermined rotation speed corresponding to the amount of air increased by opening the damper 52 at the same time when the driving of the damper 52 is started. During the driving of 52, this rotation speed is maintained and the supply amount of the flow rate pump 58 is kept constant.

Accordingly, the combustion state during driving of the damper 52 is stabilized by correcting the combustion air amount in advance at the same time as the driving, with respect to the air amount fluctuating due to the opening / closing operation of the damper 52.
It is possible to reliably prevent abnormal combustion such as blowout and generation of soot.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a vaporization type petroleum combustion apparatus according to the present invention will be explained based on an embodiment shown in the drawings. Reference numeral 1 is a horizontal bowl-shaped vaporizer made of aluminum die cast, the front surface of which is closed by a fuel injection nozzle 2 and a lid 4 equipped with an outlet 3 for primary air, and a partition wall 5 which divides the bottom into two parts. The mixed gas outflow port 6 is formed.

The carburetor 1 has an inner surface facing the fuel injection nozzle 2 which is formed perpendicularly to the fuel injection nozzle 2 to form a vertical vaporization surface 7, and a portion to which the fuel oil is sprayed has a uniform diffusion of the fuel oil. To form a flat surface 8, and a plurality of beads 9 having different lengths are arranged around the flat surface 8 in a horizontal direction and in parallel with each other to form a meandering path 10 for the flowing fuel oil. Is formed.

Since the flat surface 8 and the meandering path 10 are formed with one injection hole 11 on each side of the fuel injection nozzle 2, one on each side of the vertical vaporization surface 7 facing each other. Are provided one by one.

Reference numeral 12 is a U-shaped seal cast in the vaporizer 1.
A heating heater composed of a heater, which protrudes from above the vertical vaporization surface 7 toward the fuel injection nozzle 2 side, and an upper side wall 13 which covers a space above the vertical vaporization surface 7 and a vertical projection from below the vertical vaporization surface 7. It is cast into the lower side wall 14 forming the outflow port 6.

Reference numeral 15 denotes a trapezoidal guide wall provided at the final end of the meandering path 10 of the carburetor 1 and having a trapezoidal shape when seen from a plane. The guide gas at the bottom is a mixture gas of the vaporized gas formed in the carburetor 1 and the primary air for combustion. The two outlets 6 are smoothly divided and guided.

Reference numeral 16 is a mixing chamber made of aluminum die-cast provided in the lower part of the vaporizer 1, and is a rectifying chamber which is communicated with the outflow port 6 and is depressed one step downward so as to rectify the mixed gas so as to have a large capacity. And a plurality of gas chambers 19 which communicate with the rectifying chamber 17 and are formed in a tapered shape so as to alternately communicate with a secondary air chamber 18 downwardly between the gas chambers 19 and the rectifying chamber 1.
7 Auxiliary heater 2 consisting of U-shaped seed heater at the bottom
0 is cast, and the mixing chamber 16 is preheated by being energized only for a certain time during preheating.

Further, a heat-resistant paint is applied to the inner surface of the mixing chamber 16 to form a finely roughened coated surface 21 so that the flow rate of the mixed gas is made uniform and the jetting speed of the mixed gas is made uniform and rectification is promoted. It measures.

Reference numeral 22 is a straightening plate provided at the entrance of each gas chamber 19 so as to hang down from above. The straightening plate is formed by alternately forming notches and bent pieces on one plate. / 6
By closing the above from above, the wind force sent to the gas chamber 19 is suppressed and a uniform flame is formed overall.

Reference numeral 23 is a burner portion formed on the gas chamber 19 and the secondary air chamber 18 of the mixing chamber 16 on the rear side of the vaporizer 1, and is a convex flame hole fixed on the gas chamber 19. Part 24
And a secondary air supply portion 25 formed by a recess between the adjacent flame hole portions 24 and communicating with the secondary air chamber 18, and the flame hole portion 24 has a top portion extending substantially from the central portion to the side wall. The elongated reverse L-shaped flame holes 26 are formed alternately in the left-right direction along the longitudinal direction, and a secondary air hole 27 communicating with the secondary air chamber 18 is further formed at the bottom of the secondary air supply unit 25. The small holes formed in the flange portion 28 of the portion 24 are formed by being overlapped with each other, so that the secondary air can be rectified reliably while keeping a distance from the flame holes 26.

Reference numeral 29 is a flame holding guide fixed to both sides of the flame hole portion 24, and is formed in the flame hole 26 by bending the upper portion facing the flame hole 26 obliquely upward on the side opposite to the flame hole 26. The secondary air supplied from below is guided while suppressing the spread of the flame.

Reference numeral 30 denotes a heat-resistant rectifying net provided in the flame hole portion 24, which is formed by braiding a wire material having a wire diameter of 0.29 mm into 36 mesh, and is used for the final rectification of the mixed gas ejected from the flame hole 26. It is something to do.

Reference numeral 31 is a vertically long heat absorbing fin projecting from the rear surface of the carburetor 1 onto the burner portion 23, and is divided into a plurality of parts in order to increase the contact area with the combustion gas and increase the amount of heat back. At the time of combustion, the heat back of the combustion heat is used as the heat of vaporization to save the electric power of the heating heater 12, and the upper end thereof is an inclined portion 32 which is inclined downward toward the burner portion 23 side and is raised. It helps to remove the coming combustion heat.

Further, the flame holes 24 are disposed below the heat absorbing fins 31, and the flame holes 24 between the heat absorbing fins 31 are about 10 times as large as the other flame holes 26. Forming a large flame hole 33 consisting of two quadrangles
In addition, one vertical groove 34 is provided in the center of the projecting end surface of each heat-absorbing fin 31 so as to extend from the lower end to the upper end, and due to the spread of the flame formed in the large flame hole 33 at the time of high-power combustion, this vertical groove 34 is formed.
In addition, the flame is introduced so that the heat absorption area is increased.

Reference numeral 35 is an L provided above the heat absorbing fins 31.
Approximately 2 above the heat absorbing fins 31 from the carburetor 1 side with a letter-shaped restraint plate.
/ 3 to cover the space between the heat-absorbing fins 31 and the vertical groove 34, and suppress the rising force of the combustion heat that rises between the heat-absorbing fins 31. Also, when the entire upper part of the heat-absorbing fins 31 is covered. Alternatively, the restraining plate 35 itself may be provided with slits or holes to adjust the restraining force.

Reference numeral 36 denotes an uneven surface formed by continuously forming a plurality of R-shaped convex portions in the lateral direction on the rear wall of the carburetor 1 between the heat absorbing fins 31, which increases the heat absorbing area and controls the rising force of combustion heat. I try to get enough heat back,
In particular, since it has an R shape, it is possible to smoothly suppress only the ascending force of the combustion heat without causing turbulence.

Reference numeral 37 indicates the rear surface of the carburetor 1 and exposes the burner portion 2
3 is an upper open combustion chamber that surrounds the upper part of FIG. 3, the outer periphery of which is covered by a cover frame 38 at predetermined intervals, and the wall surface above the heat absorbing fins 31 has a plurality of first rows arranged at regular intervals.
A first air ejection portion 41 including an ejection hole 39 and a first guide piece 40 which is closed at the front of the first ejection hole 39 and opened upward is provided, and secondary air is ejected into the combustion chamber 37 to generate a flame. This is to prevent wraparound.

Further, at the lower part of one side wall of the combustion chamber 37 facing the rear surface of the carburetor 1, a plurality of second rows are arranged at regular intervals.
A second air ejection portion 44 including an ejection hole 42 and a second guide piece 43 which is closed at the front of the second ejection hole 42 and is open at the upper side.
Is provided, secondary air is jetted into the combustion chamber 37 to suppress the deviation of the flame, and the one-side wall is prevented from being burnt by the air-caten effect.

The predetermined distance between the combustion chamber 37 and the cover frame 38 is vertically divided by the partition plate 45 from the upper end of the outer periphery of the mixing chamber 16 into the combustion chamber 37 side and the mixing chamber 16 side, and the upper portion thereof. 37, a cooling flow path 46 for cooling and a heat retention flow path 47 for keeping the temperature in the lower part of the mixing chamber 16 are provided. The cooling flow path 46 and the heat retention flow path 47 are on the opposite side of the vaporizer 1 from each other.
It communicates only at the tip.

Reference numeral 48 denotes a blower whose rotation speed is controlled according to the amount of combustion. The blower 48 communicates with the air passage 49 at a right angle through an air outlet 50 provided on the upper surface of the air passage 49, and the air passage 49 is vaporized. The fuel injection nozzle 2 is connected to a guide passage 51 having one end opened at the ejection port 3 of the container 1 and fixed upward, and primary air for combustion is supplied through the guide passage 51.

Further, the combustion air that has not flowed into the guide passage 51 in the air passage 49 passes through the outer periphery of the carburetor 1 to cool the combustion chamber 37, and then passes through the heat-retaining passage 47 from the secondary air hole 27 to the bar.
The secondary air for combustion is supplied to the corner portion 23.

Reference numeral 52 is an inverted L-shaped damper provided on the windward side of the guide passage 51, and is erected by driving a stepping motor 53 in the Lo combustion range B so as to block more than half of the blower port 50. The ventilation path 49 is defined as an ventilation area of only the ventilation gap 54 on the outer periphery of the damper 52 and the four ventilation holes 55 with a diameter of 4 mm provided on the extension of the guide path 51. The optimum amount of combustion air is set according to the combustion, and in the Hi combustion range A, the blower port 50 is used.
It is positioned to incline downward and guides the air flow to prevent turbulence.

Reference numeral 56 denotes a drive shaft connected to the stepping motor 53, which has a lower end of the damper 52 penetratingly fixed thereto and is rotatably supported by a shaft supporting portion 57.

Reference numeral 58 is a flow rate pump for pressure-feeding the fuel oil to the fuel injection nozzle 2 through the oil feed pipe 59. The flow rate pump 58 works in conjunction with the blower 48 and the damper 52 to change the fuel oil supply amount according to the load.
The combustion amount of the burner unit 23 is controlled from Hi to Lo combustion.

Reference numeral 60 is a stopper for restricting the damper 52 in a standing state, and 61 is a heat shield plate.

Next, the block diagram of the electric circuit shown in FIG. 8 will be described. When a heat request regarding the combustion amount of the burner section 23 is input to the microcomputer 62, the microcomputer 62 calculates and controls the rotation speed of the blower 48. In addition, the flow rate pump 58 is controlled by switching the frequency and two on-time periods, and when switching between the Hi combustion range A and the Lo combustion range B, the stepping motor 53 is driven to control the opening and closing of the damper 52.

Further, the microcomputer 62 has 44000 Kcal.
/ h ~ 14000 Kcal / h for Hi combustion range A, 16000 Kc
al / h to 8000 Kcal / h is Lo combustion range B, On time of flow pump 58 in Hi combustion range A is 8.7 ms, On time of Lo combustion range B is 4.4 ms, and flow rate in each combustion range The frequency of the pump 58 and the rotation speed of the blower 48 are stored in advance.

Further, the control of the flow rate pump 58 by the frequency and the two on-times is made lower by the drive frequency control related to the increase and decrease of the supply amount by the vertical movement control of the plunger (not shown) of the flow rate pump 58. Pulsating combustion occurs when it exceeds, and there is a region where the supply amount does not increase when it is raised too much,
This is because the on-time for controlling the stroke of the plunger needs to be switched as described above in order to obtain the required calories.

Next, the operation of the embodiment of the present invention will be described. When the heater 12 for heating is energized to heat the vaporizer 1 to a predetermined temperature, this is detected by a temperature sensor (not shown) provided in a proper position, and the blower 48 and the flow rate pump 58 are driven. Fuel oil is supplied to the carburetor 1 from the fuel injection nozzle 2, and primary air for combustion is supplied from the ejection port 3.

In the carburetor 1, the fuel oil injected from the fuel injection nozzle 2 collides with the flat surface 8 of the vertical vaporization surface 7 and has no unevenness, so that it diffuses uniformly to the surroundings. There is also a wind force of the primary air supplied on the bead 9 and it sequentially moves along the meandering path 10, and a sufficient vaporization time is reached, vaporization is promoted, and it is supplied by the unevenness of the bead 9. The primary air also causes a turbulent flow and is sufficiently mixed with the vaporized gas, so that a good mixed gas can be obtained.

Therefore, by the vertical vaporizing surface 7, a light and compact vaporizer 1 can be obtained, a small and powerful combustion device can be obtained, and a sufficient mixed gas can be always formed without lowering the vaporization ability. It is a thing.

The vaporized gas vaporized on the vertical vaporizing surface 7 is
The primary air bounced back by colliding with the vertical vaporization surface 7 flows to the upper and lower side walls 13 and 14 provided with the heating heater 12 in the horizontal bowl-shaped vaporizer 1.
Since No. 4 is sufficiently heated by the heating heater 12, the vaporization of the vaporized gas is further promoted, and the primary air is also well heated. Moreover, the vaporizer 1 is in the shape of a horizontal bowl and has the vaporized gas and the primary air. Does not flow out immediately, but stays in the vaporizer 1 to some extent and is sufficiently mixed, and then flows out from the outlet 6.

On the other hand, the mixed gas flowing out from the outlet 6 flows into the mixing chamber 16, which is heated for a certain period of time by the auxiliary heater 20 which is energized simultaneously with the preheating of the vaporizer 1. Since the high temperature preheated state is maintained, the mixed gas that has flowed in does not liquefy.

Then, the mixed gas promotes rectification in the rectification chamber 17, and immediately immediately after being divided into a plurality of gas chambers 19 and finely divided, it flows into the gas chambers 19. Due to the fine irregularities and the tapered shape by the coating surface 21 on the inner wall surface, the flame hole portion is formed. The ejection speed of the mixed gas ejected from the flame holes 26 of 24 is uniform irrespective of the longitudinal direction,
In addition, the mixed gas is rectified 3 immediately before being ejected from the flame hole 26.
Combustion is started by passing through 0, finally being rectified and ejected, and appropriately ignited by an ignition means (not shown).

Between the heat absorbing fins 31 at the time of combustion, the large flame holes 33 of the flame hole portion 24 are supplied with a large amount of the mixed gas and burn with a larger flame than the other flame holes 26, so that the heat absorbing fins 31 are separated from each other. It is possible to obtain a certain amount of good heat-back even during Lo combustion in which a flame dedicated to the heat-back is formed. Further, during Hi-combustion, due to the spread of the flame formed in the large flame hole 33. , Adjacent heat absorbing fin 31
Flame enters from both sides into the vertical groove 34 of
Since the flame passes through the inside from the lower end to the upper end, the endothermic area is substantially increased, and the vaporization amount increases.
Even when i is burned, a sufficient amount of heat back is obtained and good burning can be performed.

Therefore, during Lo combustion in which a large amount of heat back is not required, it is possible to prevent melting of the carburetor 1 due to normal heat back and too much heat, and Hi combustion in which a large amount of heat back is required. Occasionally, the amount of heat back can be naturally increased by utilizing the spread of flame and the vertical groove 34, that is, the heat absorption area can be automatically increased or decreased according to the heat power, and good vaporization can always be performed with optimal heat of vaporization. Good combustion can be maintained and, of course, it is possible to surely save power without having to energize the heating heater 12 after the start of combustion.

Further, the combustion heat rising between the heat absorbing fins 31 during combustion and in the vertical groove 34 is suppressed in its rising force by the upper restraining plate 35, and is discharged obliquely upward from the inclined portion 32 at the upper end of the heat absorbing fin 31. And therefore the ramp 3
The combination of 2 and the suppression plate 35 allows the combustion heat to easily escape from between the inclined portion 32 and the suppression plate 35 without causing hot air to be trapped between the heat absorbing fins 31 and the vertical groove 34 to cause an abnormal heating state. By doing so, a good amount of heat back is obtained while suppressing the rising force to some extent.

On the other hand, in the Hi combustion range A, as shown in FIG. 9, at the point a where the combustion amount is the maximum in the Hi combustion range A, the damper 52 is opened, the rotation speed of the blower 48 is set to the maximum state, and the combustion amount is reduced. If the frequency of the flow rate pump 58 is decreased and the rotation speed of the blower 48 is decreased to reach the minimum b point of the Hi combustion range A, the damper 52 is also maintained in this state.
Is still open.

When the combustion amount is further decreased from the point b, the damper 52 is closed and the rotation speed of the blower 48 is increased to reach the point c'in the Lo combustion range B and further to the point d. On the contrary, when the damper 52 is opened, when the point c of the maximum combustion amount in the Lo combustion range B is reached and the combustion amount is further increased, the damper 52 is opened and the rotation speed of the blower 48 is increased. If it is lowered, it is moved to the b'point of the Hi combustion range A, and the damper 52 is opened / closed to A, B2.
A wide combustion variable range can be obtained in one stable combustion region.

Further, FIG. 1 shows the opening / closing driving state of the damper 52.
In detail, as shown in FIGS. 0 to 13, first, in the closing direction of the damper 52, during the combustion operation in the Hi combustion range A, Lo
When a heat request to the combustion range B side occurs (step 6
3) Then, the process proceeds to step 64, where the microcomputer 62 sets the blower 4
8 and the flow rate pump 58 are controlled to perform the minimum combustion (point b) in the Hi combustion range A, and the driving of the damper 52 is started in step 65, and the rotation speed of the blower 48 is once increased in step 66. 1742 rpm → 250
The rotational speed is increased to 0 rpm and this rotational speed is continued until the driving of the damper 52 in step 67 is stopped.

The flow rate pump 58 also remains in the minimum combustion state in the Hi combustion range A while the damper 52 is being driven, that is, in this drive state, the combustion amount is constant with the rotational speed of the initial blower 48 slightly increased. In this state, the flow rate pump 58 is changed to the frequency and on-time of the Lo combustion range B in step 68, and then the process proceeds to step 69 to control the combustion amount according to the heat demand. At this time, the rotation speed of the blower 48 is far lower than the corrected predetermined rotation speed, and is on the descending side.

Next, in the opening direction of the damper 52, when the heat request to the Hi combustion range A side is generated during the combustion operation in the Lo combustion range B (step 70), the process proceeds to step 71, and the microcomputer 62 causes the blower 48 and the flow rate to flow. Control the pump 58 to Lo
The maximum combustion (point c) in the combustion range B is performed, and the drive of the damper 52 is started in step 72, and the rotation speed of the blower 48 is once lowered in step 73.
The speed is reduced from 1 rpm to 2000 rpm, and this rotation speed is continued until the driving of the damper 52 in step 74 is stopped.

The flow rate pump 58 also remains in the maximum combustion state in the Lo combustion range B while the damper 52 is being driven, that is, in this drive state, the combustion amount is constant when the rotational speed of the blower 48 at the beginning of driving is slightly lowered. In this state, the flow rate pump 58 is changed to the frequency and on-time of the Hi combustion range A in step 75, and then the process proceeds to step 76 to control the combustion amount according to the heat demand. At this time, the rotation speed of the blower 48 becomes higher at a rotation speed much higher than the corrected predetermined rotation speed, and the rotation speed after the driving of the damper 52 is corrected in the opposite direction to the control direction. .

Therefore, the combustion air amount is corrected by correcting the change in the combustion air amount that occurs during the opening / closing drive of the damper 52 with the correction value obtained in advance by the experiment and by correcting the rotation speed of the blower 48 at the same time when the driving of the damper 52 is started. It is possible to reliably prevent abnormal combustion such as blowout of flames and the generation of soot caused by changes, and to smoothly switch from the Hi combustion range A to the Lo combustion range B and vice versa.

The opening / closing operation of the damper 52 is performed in about 4 seconds, and the rotation speed correction of the blower 48 especially in the closing direction is performed at the same time as the driving of the damper 52 is started because of the relation with the increase of the blowing pressure. Even if it is carried out with a slight delay, a good effect can be obtained.

[0052]

In summary, the present invention is a carburetor equipped with a heating heater for vaporizing fuel oil, and a blower for supplying primary air for combustion to the carburetor and secondary air for the burner section. A blower passage that communicates the blower port of the blower with the carburetor and the burner section; and a guide passage that guides primary air to the jet port of the carburetor that communicates with the blower passage. A damper for controlling the cross-sectional area of the blower passage at two positions of opening and closing is provided on the windward side of the guide passage, and at the start of driving the damper,
The rotation speed of the blower is corrected to a predetermined rotation speed on the rising side in the closing direction and to a predetermined rotation speed on the falling side in the opening direction, and this rotation speed is maintained until the damper driving is completed. Not only can the combustion variable range be expanded by the opening and closing action of, but abnormal combustion due to changes in the combustion air amount that occurs during the opening and closing drive of this damper can also be reliably prevented, and the minimum combustion to the maximum combustion is always maintained. Good combustion is obtained and it is extremely convenient to use.

[Brief description of drawings]

FIG. 1 is a sectional view of a vaporization type petroleum combustion device according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view of the combustion chamber.

FIG. 3 is a sectional view of the burner portion.

FIG. 4 is a cross-sectional view of the air duct.

FIG. 5 is an exploded perspective view of the burner portion.

FIG. 6 is an enlarged sectional view of the burner portion.

FIG. 7 is a front view of the vaporizer.

FIG. 8 is a block diagram of the electric circuit of the main part.

FIG. 9 is a characteristic diagram showing the relationship between the combustion amount and the blower rotation speed.

FIG. 10 is an explanatory diagram showing an operating state of each part when the damper is driven in the closing direction.

FIG. 11 is an explanatory diagram showing an operating state of each part when the damper is driven in the opening direction.

FIG. 12 is a flowchart when driving the damper in the closing direction.

FIG. 13 is a flowchart when driving the damper in the opening direction.

[Explanation of symbols]

1 vaporizer 3 spouts 12 Heater for heating 23 Burner section 48 blower 49 air duct 50 Blower 51 guide way 52 damper 58 flow pump

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Takahiro Kimura 7-7 Higashishinpo, Sanjo City, Niigata Prefecture Corona Co., Ltd. (56) Reference JP-A-8-21606 (JP, A) JP-A-63-99414 ( JP, A) Actual development Sho 63-80439 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F23N 3/08 F23D 11/10

Claims (2)

(57) [Claims] 1. A vaporizer equipped with a heating heater for vaporizing fuel oil, a blower for supplying primary air for combustion to the vaporizer and for supplying secondary air to a burner section, and a blower for the blower. An air blowing passage that connects the air outlet to the carburetor and the burner portion, and a guide passage that guides the primary air is provided at the jet outlet of the carburetor that communicates with the air blowing passage. Has
A damper for controlling the cross-sectional area of the blower passage at two positions of opening and closing is provided, and at the start of driving of the damper, the rotation speed of the blower is a predetermined rotation speed on the up side in the closing direction and a predetermined rotation speed on the down side in the opening direction. The gasification type petroleum combustion device is characterized in that this rotation speed is maintained until the end of drive of the damper. 2. The vaporization type petroleum combustion apparatus according to claim 1, wherein a supply amount of a flow pump for supplying fuel oil is kept constant during the driving of the damper.