JPH07127848A - Kerosene burner device - Google Patents

Abstract

PURPOSE:To permit stabilized combustion by reducing the fluctuation of kerosene supplying pressure for a spray nozzle when a reciprocating pump is employed. CONSTITUTION:A kerosene burner device is provided with a kerosene spray nozzle 2, a kerosene supplying pipeline 10, an AC driven first reciprocating pump 21, a DC pulse driven flow rate controlling opening and closing valve 22, an AC driven second reciprocating pump 23 and a return pipeline 11. The DC driving pulse of the flow rate-controlling opening and closing valve 22 is provided with the same period as the first reciprocating pump 21 while the center of the DC driving pulse is advanced from the center of the driving wave of the first reciprocating pump 21 by a given phase corresponding to the delay of change of hydraulic pressure with respect to the kerosene-supplying pipeline 10 of the return pipeline 11. The second reciprocating pump 23 is driven at the same priod and same phase as the first reciprocating pump 21 while the ignition timing of the driving wave is corrected in accordance with a difference between a hydraulic pressure, detected by a hydraulic pressure sensor 13 provided in the kerosene supplying pipeline 10 before the kerosene spray nozzle 2, and the average value of the detected hydraulic pressures.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION This invention relates to petroleum burner equipment.

[0002]

2. Description of the Related Art Conventionally, as this kind of petroleum burner apparatus, an apparatus described in Japanese Patent Application Laid-Open No. 2-110210 has been provided. This device is equipped with two pumps in series in the oil supply line to the spray nozzle to supply oil to the spray nozzle.

[0003]

However, in the petroleum burner apparatus as described above, when the two pumps are reciprocating type pumps such as electromagnetic pumps, the two pumps independently perform reciprocating operation. The oil supply pressure to the spray nozzle, and hence the spray pressure, tends to be unstable, and the combustion noise becomes a noise.

Therefore, the present invention solves the above-mentioned drawbacks of the conventional apparatus, reduces fluctuations in the oil supply pressure to the spray nozzle when a reciprocating pump is used, and provides an oil burner apparatus capable of performing stable combustion. For the purpose of provision.

[0005]

To achieve the above object, an oil burner apparatus of the present invention comprises an oil spray nozzle, an oil supply line for supplying oil from an oil tank to the spray nozzle, and the oil spray nozzle. An AC-driven first reciprocating pump, a DC pulse-driven flow control on-off valve, and an AC-driven second, which are sequentially provided from a side closer to the petroleum spray nozzle of the supply line.
An oil burner device comprising at least a reciprocating pump, and a return line connected from the oil spray nozzle to an oil supply line between the first reciprocating pump and the flow control on-off valve, Regarding the flow rate control on-off valve, the cycle of the DC drive pulse is the same as that of the first reciprocating pump, and the center of the DC drive pulse is from the center of the drive wave of the first reciprocating pump to the return line. Of the oil supply line, the second reciprocating pump is driven in the same cycle and in the same phase as the first reciprocating pump, and the oil is moved in the same phase. The first feature is that the ignition timing of the drive wave is corrected in accordance with the deviation between the oil pressure detected by the oil pressure sensor provided in the oil supply pipeline before the spray nozzle and its average value. That. In addition to the first feature, the petroleum burner device of the present invention uses a commercial power source to drive the first and second reciprocating pumps, and controls the flow control on-off valve calculated from the required heat of combustion. The second feature is that the DC drive pulse width is automatically converted according to the operating frequency of the commercial power source.

[0006]

According to the first aspect of the present invention, the oil from the oil tank is supplied to the oil supply pipeline by the two AC driven reciprocating pumps being driven and the DC pulse driven flow control valve. The oil is sent to the oil spray nozzle, atomized and used for combustion, and part of the oil is sprayed from the oil spray nozzle back to the oil supply line through the return line. Since the change in oil pressure of oil in the return pipe (change in the amount of return oil) occurs with some delay, there is a tendency for fluctuations (maximum, minimum) in the combined total oil supply pressure and supply amount to increase. In the present invention, the center of the DC drive pulse of the flow rate control on-off valve is set to the center of the drive wave of the first reciprocating pump by a constant phase corresponding to the delay of the hydraulic pressure change of the return pipeline to the oil supply pipeline. By advancing the oil, large fluctuations in oil pressure (oil supply amount) are suppressed, and oil is supplied at a stable supply pressure and supply amount. In addition, the ignition timing of the drive wave is corrected according to the deviation between the oil pressure detected by the oil pressure sensor provided in front of the oil spray nozzle and its average value. It is possible to further suppress fluctuations in the hydraulic pressure supplied to the spray nozzle. According to the second feature of the present invention, in addition to the operation of the first feature, a flow control on / off valve for obtaining a necessary heat quantity for either one of the frequencies of 50 Hz and 60 Hz. The DC drive pulse width is calculated, and when the frequency of the commercial power supply actually loaded is detected thereafter, the DC drive pulse width is automatically converted to correspond to the actual commercial frequency used. That is, for example, the DC drive pulse width of the flow control on-off valve calculated on the premise of 50 Hz is 5 / as a conversion constant when the commercial frequency actually used is 60 Hz.
When multiplied by 6, it is converted to a pulse width at 60 Hertz. By automatically storing this conversion constant in the controller, automatic conversion can be performed. By doing this,
It is possible to easily obtain the required DC drive pulse width of the flow rate control on-off valve according to the frequency of the commercial power source.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is an overall configuration diagram showing an embodiment of a petroleum burner device of the present invention, and FIG. 2 is an electric circuit diagram of essential parts of the present invention device.
FIG. 3 is a drive waveform diagram of an AC driven reciprocating pump and a flow rate control on-off valve, FIG. 4 is a flow chart for explaining the operation control operation of the device of the present invention, FIG. 5 is a flow chart for explaining the control of the flow rate control on-off valve, and FIG. 6 is a flowchart illustrating an operation for detecting the drive frequency of the reciprocating pump. FIG. 7 is a flowchart illustrating an example of correcting the ignition timing of the drive wave of the second reciprocating pump.

First, the overall construction of the embodying apparatus will be described with reference to FIG. Reference numeral 1 denotes a combustion can body, and a petroleum spray nozzle 2 faces the inner space of the combustion can body 1. The fan motor 3 blows air from around the petroleum spray nozzle 2 into the combustion can body 1. Combustion can 1
A heat exchange section 5 continuous with the water inlet pipe 4 and the hot water outlet pipe 6 is provided in the upper part of the inner space. The water inlet pipe 4 is provided with a water flow rate sensor 7 and a water temperature sensor 8. Reference numeral 9 is an igniter for ignition.

An oil supply line 10 is connected to the oil spray nozzle 2.
Further, the oil spray nozzle 2 is provided with a return line 11 as a return type nozzle. In the oil supply pipe line 10, from the side closer to the oil spray nozzle 2, an AC-driven first reciprocating pump 21, a DC pulse-driven flow control on-off valve 22, and an AC-driven second reciprocating pump. 23 and the return line 11 is connected between the first reciprocating pump 21 driven by AC and the flow control on-off valve 22 driven by DC pulse. An oil pressure sensor 13 for detecting the oil pressure of the oil supplied to the oil spray nozzle 2 is provided in the oil supply pipeline 10 in front of the oil spray nozzle 2. Reference numeral 30 denotes a controller for controlling the entire oil burner device, which inputs a command from the remote controller 40 and information from the incoming water flow rate sensor 7, the incoming water temperature sensor 8, the hydraulic pressure sensor 13 and other sensors, and the pumps 21 , 23, the flow control on-off valve 22, etc., and outputs a predetermined operation command to other members.

Referring to FIG. 2, the controller 30 has a built-in microcomputer 31 to issue an operation command to each section. Half-wave rectification is supplied to the first reciprocating pump 21 from an AC commercial power source 50 of 100 V through a diode 51. A drive wave is supplied to the second reciprocating pump 23 from the commercial power source 50 through the phase control circuit 53.
Further, a zero-cross point detection circuit 54 is provided, and its detection signal is input to the microcomputer 31. On the other hand, a DC pulse is supplied from the DC power source 60 to the relay switch R ₁ and the flow rate control on-off valve 22 via the transistors 61 and 62, respectively. By controlling the base currents of the transistors 61 and 62 with the microcomputer 31 of the controller 30, the flow control on-off valve
22 is a direct current pulse drive with a predetermined opening time,
The operation of the reciprocating pump 21 is started and ended. The ignition circuit 63 of the second reciprocating pump 23 is provided in the circuit of the DC power supply 60 and is controlled by the microcomputer 31. This firing circuit
By controlling 63 by the microcomputer 31, the second reciprocating pump 23 is driven through the phase control circuit 53 while controlling the ignition timing.

The operation control of the device by the controller 30 will be described. First, referring to FIG. 4, when there is an operation command for the device (Yes in S1), the controller 30 turns on the fan motor 3, the igniter 9, and further the second reciprocating pump 23 and the flow rate control opening / closing. The valve 22 is opened and closed with the initial value, and the first reciprocating pump 21 is turned on (S2). With this, if ignited (Yes in S3), igniter 9
Is turned off (S4), the opening / closing operation control of the flow rate control opening / closing valve 22 (S5) and the operation control of the second reciprocating pump 23 are started (S6).

The opening / closing operation control of the flow rate control opening / closing valve 22 is shown in FIG.
Referring to, first, the controller 30 inputs the water flow rate Q input from the water flow rate sensor 7, the set hot water temperature T _S input from the remote controller 40, and the water temperature T input from the water temperature sensor 8.
_The required combustion heat quantity is calculated from _c (S11), and from the necessary combustion heat quantity, the frequency of the commercial power source, that is, the first reciprocating pump
Assuming that the drive frequency of 21 is, for example, 50 Hz, the opening time of the flow rate control on-off valve 22, that is, the DC pulse width W is calculated and determined (S12). Then, when the actually detected drive frequency (how to detect it later in FIG. 6) is 60 hertz, the pulse width is automatically converted by multiplying the calculated pulse width W by 50/60 (S13). ), The DC pulse width W of the flow rate control on-off valve 22 is determined. If the actual power source used is 50 Hz, conversion is not necessary. Next, the opening start time T _ON of the flow rate control on-off valve 22 is calculated by the following formula from the cycle C of the driving AC power supply of the reciprocating pump 21 and the opening time W (S).
14). T _ON = C / 4−W / 2−α Then, from the zero cross point (ZC point) of the driving AC power supply to T
At the time when _{ON has} passed, that is, T _ON time (YES in S15), a DC pulse is applied to the flow rate control on-off valve 22 through the transistor 62 to open the valve 22 for the opening time W (S).
16). When the opening time W has elapsed (YES in S17), the valve 22 is closed (S18). And set outlet temperature T
_The steps S15 to S18 are repeated while _S , the incoming water temperature _Tc , and the incoming water flow rate Q are not changed.

The relationship between the opening time W of the flow rate control on-off valve 22, the fixed time and the opening start time T _ON, and the cycle C of the driving AC of the reciprocating pump 21 is as shown in FIG. The cycle of the opening time W of the control opening / closing valve 22 and the cycle C of the driving AC of the reciprocating pumps 21 and 23 are made the same, and the central time of the opening time W of the flow control valve 22 is set to the first reciprocating pump 21. The driving AC is advanced by a constant value, that is, a constant phase α from the time of 1/4 cycle from the zero cross point. The constant phase α is the oil spray nozzle against the change in the oil supply pressure generated in the oil supply line 10 when the first reciprocating pump 21 starts pushing the oil from the zero cross point (ZC point). The time delay of the change in hydraulic pressure caused by the return of oil from 2 through the return pipe 11 is previously obtained by experiment, and this is given as the phase value α to determine the opening / closing timing of the flow control on-off valve 22. Try to advance by α. By doing so, the total amount of changes in the oil pressure in the oil supply line due to the driving of the two reciprocating pumps and the change in the oil pressure in the return line 11 that causes a certain delay is obtained as a total amount. It is possible to finely control the occurrence of large maximum and minimum peaks in the supplied hydraulic pressure,
As a result, oil pressure fluctuations in oil supply (oil supply amount) are suppressed, and oil is supplied at a stable supply pressure and supply amount. Of course, by making the two reciprocating pumps in the same cycle and in the same phase, fluctuations in hydraulic pressure and flow rate are performed in a constant and stable state,
A stable oil supply is provided.

In the above description, for the calculation of the driving AC cycle C of the first reciprocating pump 21, referring to FIGS. 2 and 6, the controller 30 detects the AC zero-cross point by the AC power source 50 in advance. , The time from the zero-cross point to the zero-cross point is measured (S21).
Calculate the frequency of. Of course, when a commercial power source is used, it may be determined whether the frequency is 50 hertz or 60 hertz (S22). Then, the cycle C is calculated from the frequency and stored (S23).

Next, for the operation control of the second reciprocating pump 23, referring to FIG. 7, the drive wave of the second reciprocating pump 23 is generated in the same cycle as that of the first reciprocating pump 21. In phase,
In addition, a hydraulic pressure sensor 13 is provided in the oil supply pipe 10 in front of the oil spray nozzle 2 to control the deviation of the current value from the average value of the oil pressure of the oil supplied to the oil spray nozzle 2.
The calculation is made at 30, and the ignition timing for the drive wave of the second reciprocating pump 23 is corrected according to the deviation. That is, referring to FIG. 7, the controller 30 inputs the hydraulic pressure value P _IN from the hydraulic pressure sensor 13 during operation (S31), and the hydraulic pressure sensor 13
The average value P _AV of the detected hydraulic pressure is calculated (S32), the difference ΔP between the current value P _IN and the average value P _AV is calculated (S33), and the actual current value P _IN is a constant oil pressure higher than the average value P _AV. If it exceeds a (NO in S34), a value obtained by adding a constant phase n to the current ignition timing (ignition phase) β is set as a new ignition timing β (S35). As a result, the ignition timing of the second reciprocating pump 23 is further delayed with respect to the first reciprocating pump 21, thereby adjusting the fluctuations of the hydraulic pressure and the oil supply amount in the direction of decreasing. When the actual present value P _IN is less than the constant oil pressure b than the average value P _AV (NO in S36)
, A value obtained by subtracting a constant phase m from the current firing timing (firing phase) β is set as a new firing timing (firing phase) β (S37). As a result, the ignition timing of the second reciprocating pump 23 is further advanced with respect to the first reciprocating pump 21, and thereby the fluctuations of the hydraulic pressure and the oil supply amount are adjusted to be reduced. When the hydraulic pressure difference ΔP is a ≧ ΔP ≧ b, the ignition timing β of the second reciprocating pump 23 is maintained as it is.

[0016]

According to the petroleum burner apparatus of the first aspect of the present invention, the flow control on-off valve has a direct-current drive pulse whose cycle is the first reciprocating pump. Since the center of the direct-current drive pulse is advanced from the center of the drive wave of the first reciprocating pump by a constant phase corresponding to the delay in the change in hydraulic pressure of the return pipe with respect to the oil supply pipe, the return is made the same. It is possible to prevent an increase in fluctuations in the oil supply caused by providing the pipeline. In addition, the second reciprocating pump is driven at the same cycle and in the same phase as the first reciprocating pump, and the hydraulic pressure detected by the hydraulic pressure sensor provided in the oil supply pipeline before the oil spray nozzle is used. Since the ignition timing of the drive wave is corrected according to the deviation from the average value, the fluctuation can be suppressed according to the fluctuation of the supplied hydraulic pressure that actually occurs. It can be surely suppressed. Therefore, stable oil supply with little fluctuation in hydraulic pressure can be performed as a whole, and combustion stability and combustion noise can be reduced. According to the petroleum burner apparatus of the second aspect, in addition to the effect of the configuration of the first aspect, it is possible to easily obtain the necessary DC drive pulse width of the flow rate control on-off valve according to the frequency of the commercial power source. You can

[Brief description of drawings]

FIG. 1 is an overall configuration diagram showing an embodiment of a petroleum burner device of the present invention.

FIG. 2 is an electric circuit diagram of a main part of the device of the present invention.

FIG. 3 is a drive waveform diagram of an AC driven reciprocating pump and a flow rate control on-off valve.

FIG. 4 is a flow chart illustrating an operation control operation of the device of the present invention.

FIG. 5 is a flowchart illustrating control of a flow rate control on-off valve.

FIG. 6 is a flowchart illustrating an operation for detecting a drive frequency of a reciprocating pump.

FIG. 7 is a flowchart illustrating an example of correcting the ignition timing of the drive wave of the second reciprocating pump.

[Explanation of symbols]

 1 Combustion Can 2 Oil Spray Nozzle 5 Heat Exchange Section 6 Hot Water Pipe 10 Oil Supply Pipeline 11 Return Pipeline 13 Hydraulic Sensor 21 First Reciprocating Pump 22 Flow Control Open / Close Valve 23 Second Reciprocating Pump 30 Controller

Claims (2)

[Claims] 1. An oil spray nozzle, an oil supply pipe for supplying oil to the spray nozzle from an oil tank, and an alternating current drive first provided sequentially from the oil supply pipe closer to the oil spray nozzle. 1 reciprocating pump, DC pulse drive flow control on-off valve, AC driving second reciprocating pump,
A petroleum burner device having at least a return pipeline connected to a petroleum supply pipeline between the oil spray nozzle and the first reciprocating pump and a flow control on-off valve, wherein the flow control on-off valve is: The period of the DC drive pulse is the same as that of the first reciprocating pump, and the center of the DC drive pulse is from the center of the drive wave of the first reciprocating pump to the oil supply line of the return line. Is advanced by a constant phase corresponding to the delay of the change in hydraulic pressure with respect to the second
The reciprocating pump of (1) is driven in the same cycle and in the same phase as the first reciprocating pump, and the hydraulic pressure detected by a hydraulic pressure sensor provided in the oil supply pipeline before the oil spray nozzle and its average value The oil burner device is characterized in that the ignition timing of the drive wave is corrected according to the deviation of. 2. The first and second reciprocating pumps are driven by using a commercial power source, and the DC drive pulse width of the flow rate control on-off valve calculated from the required heat of combustion is adjusted according to the operating frequency of the commercial power source. The oil burner apparatus according to claim 1, wherein the oil burner apparatus is configured to be automatically converted.