JPH03282114A - Combustion amount varying device - Google Patents

Abstract

PURPOSE:To suppress the increase of a pressure between a nozzle and a solenoid valve by a method wherein kerosene is fed to a return type pressure spray nozzle, and when a flow rate of a part thereof is controlled by a flow rate regulating valve to return the kerosene, a shut-off valve is located on the outlet side of a pump and a solenoid having a check valve function is located in a return oil pipe, and the hole size of the valve seat of the solenoid valve is set to a value higher than that of the shut-off valve. CONSTITUTION:Kerosene is fed to a return type pressure spray nozzle with the aid of an electromagnetic type pump P, a part thereof is atomized, and a return oil amount of the rest is regu lated by a flow rate regulating valve. In which case, a shut-off valve 101 is incorporated in the pump P, a solenoid valve V having a check valve function is located in the middle of a return oil pipe, and the kerosene is returned to the upper stream side of the pump. The hole size of a valve seat 72 of the solenoid valve V is increased to a value higher than that of a valve seat 100 of the shut-off valve 101, and the solenoid valve V is closed in a slight delay from closing of the shut-off valve 101 by means of a difference in a fluid pressure during the stop of combustion of a gun type burner. Further, it is preferable that the spring constant of spring 77 through the force of which a valve body 74 of the solenoid valve V is energized in a closing direction is decreased to a value lower than that of a valve spring 105 through the force of which a valve body 102 of the shut-off valve 101 is energized in a closing direction.

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Field of Industrial Application The present invention relates to a variable combustion amount device used in domestic oil water heaters and the like.

(b) Prior Art Conventionally, as one form of this type of oil combustion device, as shown in FIG.
A pump with a built-in shutoff valve (172)
The kerosene is pressurized by the return type pressure spray nozzle (173), and is sprayed from the tip of the nozzle (173). A part of the kerosene passes through the return oil pipe (174) and is supplied to the solenoid valve (17[1]).
) and the outgoing oil pipe (71) via the flow rate adjustment valve (175).
There is a configuration in which the water is returned to the upstream side of the pump (172).

With this configuration, this oil combustion device has a return oil pipe (
By changing the valve opening degree of the flow rate regulating valve (175) provided at 174) and adjusting the amount of return oil, the amount of spray can be controlled over a wide range and the amount of combustion can be changed.

When combustion is stopped, a shutoff valve and a solenoid valve (17B) built into the pump (172) prevent kerosene from leaking from the return type pressure spray nozzle due to the head difference from the kerosene tank.

(c) Problems to be Solved by the Invention However, in the case of the above-mentioned oil combustion device, when combustion is stopped, the shutoff valve of the pump (172) closes and at the same time the solenoid valve (172) closes.
7B) is also blocked, the return pressure in the return oil pipe between the return type pressure spray nozzle (173) and the solenoid valve (17B) increases, and the amount of spray from the nozzle (173) increases. However, there was a problem that the fire extinguishing smoke and sound were generated.

(d) Means for Solving the Problems Therefore, in the present invention, an oil storage tank and a return type pressure spray nozzle are connected to each other by an outgoing oil pipe provided with a pump midway, and the nozzle and the outgoing oil pipe are connected upstream of the pump. In the combustion amount variable device, the combustion amount can be changed by increasing or decreasing the spray amount of the nozzle by connecting the side and the side through a return oil pipe provided with a flow rate adjustment valve midway, and controlling the flow rate adjustment valve. , a shutoff valve is provided on the outlet side of the pump that is energized to close at the same time as the pump is stopped, and a solenoid valve with a check valve function is provided in the return oil pipe, and the hole diameter of the valve seat of the solenoid valve is set as above. It is an object of the present invention to provide a combustion amount variable device characterized in that the hole diameter is larger than the hole diameter of a valve seat of a shutoff valve.

Another feature is that the spring constant of the valve spring that biases the electromagnetic valve body in the valve closing direction is smaller than the spring constant of the valve spring that biases the valve body of the stop valve in the valve closing direction.

(e) Action/effect According to the present invention, the following effects are produced.

That is, in the present invention, since the hole diameter of the valve seat of the solenoid valve is made larger than the hole diameter of the valve seat of the shutoff valve provided in the pump, the fluid pressure acting on the valve body of the solenoid valve increases, and the same The plunger that operates the valve body moves slowly in the valve closing direction, and when combustion is stopped, the electromagnetic valve closes after the pump shutoff valve closes.

Also, by making the spring constant of the valve spring that biases the valve body of the solenoid valve in the valve closing direction smaller than the spring constant of the valve spring that biases the valve body of the stop valve in the valve closing direction, the solenoid valve occlusion can be delayed more than the occlusion of the pump's shutoff valve.

Therefore, it is possible to suppress the return pressure in the return oil pipe between the return type pressure spray nozzle and the solenoid valve from increasing.
It is possible to prevent an increase in the amount of spray from the nozzle, and it is possible to prevent the generation of extinguishing smoke and extinguishing noise due to incomplete combustion immediately before extinguishing.

(f) Examples The present invention will be explained in detail below based on examples shown in the accompanying drawings.

FIG. 1 conceptually shows the overall configuration of an oil water heater (B) incorporating a variable combustion amount device (A) according to the present invention.

First, to explain the configuration of the combustion amount variable device (^), in Fig. 1, (T) is an oil storage tank filled with kerosene. The kerosene that has flowed into and fallen into (S) is pressurized by an electromagnetic pump (P), and the return type pressure spray nozzle (N
).

As shown in Figure 2, the return type pressure spray nozzle (N) is
A jet flow path (10) and a return flow path (11) are formed inside the kerosene, and a part of the kerosene supplied to the return type pressure spray nozzle (N) through the outgoing oil pipe (S) is atomized. The remaining kerosene is ejected from the tip nozzle opening (2), and the remainder of the kerosene is returned to the return oil pipe (R), which will be described later, through the return flow path (11).

That is, in FIG. 1, the return oil pipe (R) is connected to the outgoing oil pipe (S).
) are installed in parallel.

The return oil pipe (R) has one end connected to the return passage (11) of the return type pressure spray nozzle (N), and the other end connected upstream of the pump (P) of the outgoing oil pipe (S). The circulation channel (C
) is formed.

In addition, a flow rate adjustment valve (FC) is installed at the end of the return oil pipe (R).
or installed.

Then, by controlling the flow rate adjustment valve (FC) by the control unit (M), the return oil amount is adjusted, and the amount of spray from the return type pressure spray nozzle (N) is increased or decreased, thereby changing the combustion amount. I'm trying to do that.

In addition, in this embodiment, a shutoff valve (101) is provided in the pump (P).
In addition to the built-in solenoid valve (
v), and the opening/closing operation of the solenoid valve (v) is controlled by a pump (P
) is linked to the drive/stop operation of the

Then, the solenoid valve (V) that closes in conjunction with the stop operation of the pump (P) prevents kerosene from flowing back into the return type pressure spray nozzle (N) through the return oil pipe (R). It is possible to reliably prevent kerosene from leaking from the burner (N), and to prevent the generation of soot and sound when extinguishing a gun type burner (20) to be described later.

In Fig. 1, (Qt) is the amount of kerosene supplied from the pump (P) to the return type pressure spray nozzle (N), (
Qn) is the amount of spray from the return pressure spray nostle (N), and (Qr) is the amount of return oil passing through the return oil pipe (R).

In addition, a solenoid valve (V), a pump (P), and a flow rate adjustment valve (
The structure and operation of pc) will be explained in detail later.

Next, the configuration of the petroleum water heater (B) will be explained with reference to FIG. 1. (20) is a gun type burner in which the above-mentioned return type pressure spray nozzle (N) is disposed inside; The burner (20) has its rear connected to a fan (22) via a duct (21).

Furthermore, a damper (23) is provided within the duct (21) to adjust the amount of combustion air supplied.

(34) is an igniter.

A heat exchanger (24) is located below the gun type burner (20).
) is installed, and the water supply piping (
25), and the same water supply pipe (25) is connected to the water supply pipe (25).
A water amount sensor (2B) and a water temperature sensor (27) are attached.

On the other hand, the hot water supply pipe (
28) includes a flow rate adjustment valve (29) and a hot water temperature sensor (30).
is installed.

It is also possible to branch a bath pipe (31) from the hot water supply pipe (28), and in this case, the bath water flow sensor (3
2) and a shutoff valve (33) will be installed.

The control unit (M) also includes a microprocessor (MPU) and an input/output interface (MPU), as shown in Figure 3.
a) (b), and memory (I+) consisting of ROM and RAM.
1) and a timer (1).

The input interface (a) includes an operation switch (35), a temperature setting switch (36), and a water flow sensor (
26), a water temperature sensor (27), a hot water temperature sensor (30), and a bath water amount sensor (32).

In addition, the output interface (b) includes a pump (P).
, a solenoid valve (V), a flow control valve (FC) (29), a shutoff valve (33), a fan (22), a damper (23), and an igniter (34).

Further, as shown in FIG. 4, the solenoid valve (v) is provided with a communication flow path (71) in a cylindrical valve casing (70), and a valve seat (71) is provided on the downstream side of the communication flow path (71). 72) is provided, and a cylindrical valve body advancing/retracting rod (73) is provided in the communication flow path (71) so as to be able to slide forward and backward, and the valve body advancing/retracting rod (73) is connected to a valve body driving mechanism (75). The valve body is moved forward and backward by the movement lever (73).
) is integrally molded at the tip of the valve body (74), which can be detached from the valve seat (72).

Further, (76) is a flow path provided in the valve body advancing/retracting rod (73), (77) is a valve spring that biases the valve body (74) toward the valve seat (72) in a suppressed state, (70a) (70b) is an upstream connecting portion that connects to the upstream side of the outgoing oil pipe (S), and (70b) represents a downstream connecting portion that connects to the downstream side of the outgoing oil pipe (S).

Further, the valve body drive mechanism (75) is connected to the valve casing (70).
A solenoid (78) is provided on the outer peripheral surface of the solenoid (78).
By applying a current to the valve body advancing/retracting rod (78)
3) can move forward and backward along the axis, and the valve body movement rod (73
) moves the valve body (74) at the tip to the valve seat (7).
2), so that the connecting channel (7) can be opened and closed.

In addition, (78a) is a cylindrical bobbin, (78b) is a coil,
(78c) is a cap, and (78d) is a cord.

In addition, as shown in FIG. 5, the hole diameter (D1
) is a shutoff valve (101) provided in the pump (P), which will be described later.
The hole diameter (D2) of the valve seat (100) is made larger than that of the valve seat (100).

In addition, the pump (P), as shown in FIGS. 6 to 9,
A drive section (81) is provided on a pump body (80).

As shown in FIGS. 8 and 9, the pump body (80) is connected to the upstream side of the outgoing oil pipe (S) and the nipple (82).
The suction port (83) connected via the same suction port (83)
communicates with the valve mechanism (84) via the first communication path (84).
5) and a valve chamber (86) containing the same valve chamber (86).
) and an accumulator (88) that communicates with each other via a second communication path (87).

Further, the drive unit (81) includes a hollow magnetic rod (9I) provided in a cylindrical bobbin (90) that also serves as a guide pipe, and a coil (92) provided on the outer periphery of the bobbin (90). It constitutes a solenoid (93).

A piston rod (94) is disposed directly below the magnetic rod (91) so as to be vertically slidable.
3) By applying a current to the piston rod (
94) of the pump body (80).
84) Slide the inside forward and backward to pump kerosene into the pump body (80)
In addition, it can be inhaled into a communication channel (99) which will be described later. (95) (96) are upper and lower springs, (97)
is a magnetic ring.

At this time, when the piston rod (94) retreats upward,
The left side valve (85a) of the valve mechanism (85) opens, and the right side valve (85b) closes to draw kerosene into the valve chamber (86), and the piston rod (94)
When the fuel oil advances downward, the left valve (85a) closes, and the right valve (85b) opens, forcing kerosene into the accumulator (88).

In addition, a cylindrical discharge joint (98) connected to the downstream side of the outgoing oil pipe (S) is connected to the upper part of the bobbin (90), and a communication flow path (99) is provided within the discharge joint (98). A valve seat (100) is provided in the middle of the communication flow path (99), and a shutoff valve (101) is provided within the communication flow path (99).

As shown in FIGS. 7 and 8, the shutoff valve (101) includes the valve seat (100), a valve body (102) that is separated from the valve seat (100), and a valve body (102) that is separated from the valve seat (100). 102) with the supporting piece (
A cylindrical electromagnetic movable piece (1 (14
) and a valve spring (105) interposed between the valve body (1 (12)) and the magnetic rod (9I). (D
2) is the hole diameter of the valve seat (100).

In this shutoff valve (101), when a current is applied to the solenoid (93), the electromagnetic movable piece (104) moves against the valve spring (105).
) is attracted downward against the bias of the valve body (102) and the valve seat (ioo), causing the communication flow path (99) to be in a communicating state, and applying current to the solenoid (93). When the valve body (1) is released, the pressing force of the valve spring (105)
02) contacts the valve seat (10[1) in a pressed state to close the communication flow path (99).

Therefore, when the drive of the pump (P) is stopped, the shutoff valve (+
01), kerosene does not flow to the return type pressure spray nozzle (N).

Also, in Figure 8, (106) is the upper plate, (+07) is the lower plate, (10g) is the cap, (109) (110) is O
It's a ring.

In the above configuration, the gist of the present invention is to provide a solenoid valve (
The hole diameter (DI) of the valve seat (72) of the shutoff valve (1
The reason is that the hole diameter (D2) of the valve seat (100) is made larger than that of the valve seat (100) of 01).

That is, the fluid pressure acting on the valve body (74) of the solenoid valve (V) is made greater than the fluid pressure acting on the valve body (102) of the shutoff valve (101) to operate the valve body (74). When the gun type burner (20) stops combustion, the closing valve (10
The solenoid valve (V) is closed with a slight delay after the closure in step 1).

Preferably, the hole diameter (Di) of the valve body (74) of the solenoid valve (v) is larger than 1 mm, and the stop valve (101
) The hole diameter (D2) of the valve body (102) is made smaller than one diameter.

(Q1)+;! shown in FIG. , solenoid valve (v) valve body (
This shows the change curve of the return pressure generated in the return oil pipe (R) when the hole diameter (old) of 74) is made smaller than 1 mm. The return pressure suddenly increases, then attenuates while repeating slight vibrations within a certain period of time (t1), and gradually returns to the pressure when the solenoid valve (V) is opened, forming an approximately right triangular shape shown by the - dotted line. It forms a return pressure damping zone (Z1).

The size of the area of the return pressure attenuation zone is proportional to the amount of extinguishing smoke and the magnitude of extinguishing sound.

On the other hand, (Q1) shown in FIG. 11 is a solenoid valve (V
Change in the return pressure generated in the return oil pipe (R) when the hole diameter (DI) of the valve body (74) in the case of Fig. 10 is made larger than 1 mm by approximately twice the hole diameter in the case of Fig. 10. The curve shows that the increase in return pressure when the solenoid valve (V) is closed (P2) is relatively small, and it decays while repeating slight vibrations within a certain period of time (t2), and then increases when the solenoid valve (V) is opened. The pressure gradually increases, and the flat return pressure decay zone (Z2
) is formed.

The return pressure attenuation zone (Z2) has a smaller area than the return pressure attenuation zone (Z1).

In this way, in this embodiment, the valve body (74) of the solenoid valve (V) is
) of the valve body (102) of the shutoff valve (101).
) and has a diameter larger than 1 am, the return type pressure spray nozzle (N)
It is possible to suppress the increase in the pressure in the return oil pipe (R) between the solenoid valve (V) and the solenoid valve (V), and also to stop the attenuation of the return pressure, thereby reducing the amount of spray from the nozzle (N). can be prevented from increasing, and the generation of fire extinguishing smoke and extinguishing noise can be prevented.

Further, the gist of the present invention is to adjust the spring constant of the spring (77) that biases the valve body (74) of the solenoid valve (V) in the valve closing direction to close the valve body (102> of the stop valve (101)). By making the spring constant smaller than the spring constant of the valve spring (105) that biases in the direction,
Furthermore, the solenoid valve (V) can be closed later than the shutoff valve (101).

Preferably, the spring constant of the valve spring (77) of the solenoid valve (V) is approximately half the spring constant of the valve spring (105) of the shutoff valve (101).

(Q3) shown in Fig. 12 is the valve spring (7) of the solenoid valve (V).
Return oil pipe (7) when the spring constant is set to an arbitrary value
The graph shows the change curve of the return pressure generated in R), where the return pressure increases rapidly when the solenoid valve (V) is closed (P3), and then decays while repeating slight vibrations within a certain period of time (t3). Then, the pressure gradually returns to the level at which the solenoid valve (v) was opened, and a flat return pressure damping zone (Z3
) is formed.

On the other hand, (Q3) shown in FIG. 13 is a solenoid valve (V
) shows a change curve of the return pressure generated in the return oil pipe (R) when the spring constant of the valve spring (77) in FIG. When the solenoid valve (V) is closed (P4), the return pressure suddenly increases, and then it undergoes a damped oscillation within a certain period of time (t4), quickly returning to the pressure when the solenoid valve (V) is open, as shown by the constant broken line. A flat return pressure damping zone (Z4) is formed.

This return pressure attenuation zone (z4) is smaller in area than the return pressure attenuation zone (Z3).

In this way, in this embodiment, the valve spring (7) of the solenoid valve (v) is
The spring constant of 7) is also the same as that of the valve spring (105) of the shutoff valve (101).
Since the spring constant of the solenoid valve (v) is smaller than that of the solenoid valve (v), the closing of the solenoid valve (v) can be delayed more than that of the shutoff valve (Lot), and the return type pressure spray nozzle (N) and the solenoid valve (
It is possible to reliably suppress the increase in the return pressure in the return oil pipe (R) between the return oil pipe (R) and the damping of the return pressure.

Next, an example of selection of the spring constant of the valve spring (77) of the solenoid valve (V) is as follows.

First, the general formula for determining the closing force F of the valve spring (77) is P
rXA ^: Cross-sectional area of the valve seat hole of the solenoid valve (V) Here, ■ (old) is 15 dragons ■ Return pressure (P'') at power OFF is 2.5 kg/c and fully open (see Figure 14) ) Possible ■ Return pressure (Pr) when power is OFF is 3.5 kg/cd
When the valve is half open (open state with the same area as the cross-sectional area of the valve seat hole, see Figure 15), the closing force F when the return pressure is 2.5 kg/c is also: When the return pressure is 3.5 kg/c The closing force F is also: If the seat width is H when the cross-sectional area of the valve seat hole is equal to the seat passage area, then Seat passage area - πDIXH (see Figure 15) Cross-sectional area of the valve seat hole - Since it is the passing area of the seat part, DI” −π
DIX HDI -1,5H-0,375 Therefore, the specification values of the valve spring (77) are as follows.

Stroke Closing force Omi → 44.2g or more 0.375 order 61.9g Next, the spring constant of the valve spring (77) is determined from the graph based on the specification value of the valve spring (77) determined as described above.

That is, FIG. 16a is a graph showing the relationship between the return pressure and the closing force of the valve spring (77), and (L1) is a graph showing the relationship between the return pressure and the closing force of the valve spring (77).
2) is the return pressure-closing force straight line when the hole diameter (Di) is 1.5 mi.

In addition, Figure 1.6b is a graph showing the relationship between the stroke of the valve spring (77), the valve closing force, and the seat passage area/valve seat hole cross-sectional area, and the return pressure - closing force in Figure 16a above. Using the straight line (L1), with a closing force of 3.5 kg/C-,
The stroke value at which the seat passage area/valve seat hole area is 1 is 0.375 mi (point (Px) in Figure 16b)
It can be determined that the closing force is 2.5 kg/
Since the stroke is 0 at c- (point (Po) in Figure 16b), it is easy to find the specification value straight line (L 2 ) of the valve spring that connects these two points (PX) and (PO). can.

The slope (θ) of the specification value straight line (L2) is the valve spring (77
) is the spring constant.

Further, the flow rate control valve (FC) is configured as follows.

That is, in FIG. 17, the two-part body (40a) (4
The valve casing (40), which is composed of 0b) and forms a long cylindrical body, has a communication channel (43a) horizontally penetrating the upper part of the side split body (40a). It is set up.

And the - side opening (43b) of this communication channel (43a)
As shown in Fig. 1, is connected to the upstream side of the outgoing oil pipe (S), and the other side opening (43c) is connected to the outgoing oil pipe (S).
It is connected to the downstream side.

On the other hand, a nipple (43d) is attached to the upper surface of the valve casing (40), as shown in Fig. 17, and a return oil passage (43e) provided in the nipple (43d) is connected In the middle of the flow path (43a), there is a valve seat (44) which will be described later.
A flow rate adjustment flow path (43) consisting of an L-shaped bent flow path is formed.

The inlet port (4) of the flow rate adjustment flow path (43) is
2) is connected to the upstream side of the return oil pipe (R), that is, to the return type pressure spray nozzle (N) side.

In addition, a valve seat (44) is located midway through the flow rate adjustment channel (43).
) is provided on the negative side of the valve seat (44), and a spherical valve body (45) or the valve seat (44) is disposed so as to be separable.

In this way, as described above with reference to FIGS. 1 and 17, in this embodiment, a flow rate regulating valve is installed at the point where the end of the return oil pipe (R) is connected to the upstream side of the outgoing oil pipe (S). (FC)
and install the outgoing oil pipe (
A connecting channel (43a) connecting the upstream side and downstream side of S)
and a flow rate adjustment channel (43) that connects the terminal end of the return oil pipe (R) to the middle of the communication channel (43a).

It goes without saying that the mounting position and shape of the flow rate control valve (FC) are not limited to the above, and may be any position as long as it is in the return flow path.

In addition, in this embodiment, the valve seat (44) of the spherical valve body (45)
A valve body drive mechanism (K) is provided on the side opposite to the valve casing (40), that is, at the bottom of the valve casing (40), and the valve body drive mechanism (K) has the following configuration.

The spherical valve body (45) is fitted into a circular groove (48) provided at the tip of a valve body movement rod (47) that moves back and forth on the axis of the valve casing (40).

On the other hand, the base end of the valve body advancing/retracting rod (47) is attached to the valve casing (
40) disposed within the other side divided body (40b), and
The solenoid (51) is configured by winding a coil (50) around a cylindrical bobbin (49). It is arranged.

Then, by applying a current to the solenoid (5I), the valve body advancing/retracting rod (47) is moved back and forth along the axis,
A spherical valve body (45) fitted into the tip of the valve body advancing/retracting rod (47)
can be separated toward the valve seat (44), and the amount of return oil flowing through the return oil pipe (R) can be adjusted.

In addition, as shown in FIG. 17, the flow rate control valve (FC) is
It is equipped with an advancing/retracting force adjustment mechanism (60) for adjusting the advancing/retracting force of the valve body advancing/retracting rod (47).

The advancing/retracting force adjustment mechanism (60) includes a valve casing (40).
) A cylindrical nut (61) is provided on the rear end face of the screwdriver (62), and a screwdriver (62) is screwed into the nut (6■).
Insert the tip into the cylindrical sleeve (46) so that it can move forward and backward,
Moreover, inside the cylindrical nut (61), a screw punch (62
) The spring receiver formed at the upper end of the plate (B3) and the spring receiver formed at the lower end of the valve body advancing/retracting rod (47) are the plug (
A splinter (65) is interposed between the valve casing (64) and the rear end (61a) of the cylindrical nut (6■).
o) It is fixedly connected to the bottom plate of the other side divided body (40b) by caulking.

With this configuration, by rotating the screw punch (62) by a desired means, it moves forward and backward in the axial direction of the valve casing (4o), and by moving forward and backward, the forward and backward force of the valve body movement rod (47), that is, the valve seat ( The force separating the spherical valve body (45) from the valve body (44) can be adjusted.

Furthermore, in this embodiment, since a spherical valve body (45) is used as the valve body, as shown in FIG. 18, the applied current (1)
The correlation between this and the secondary pressure (P2) generated at the inlet port (42) of the flow rate adjustment channel (43) can be changed approximately linearly.

On the other hand, through the secondary pressure (P2) and the return oil pipe (R),
Between the return oil amount (Q'') on the upstream side of the outgoing oil pipe (S) and the spray amount (Qn) from the return type pressure spray nozzle (N) (kerosene supply amount (Qt) - oil amount (Qr)) There is a linear correlation shown in FIG.

Therefore, in this embodiment, by finely adjusting the applied current (+), the return oil amount (Qr), that is, the spray amount (Qn)
can be changed linearly and accurately, allowing accurate combustion control.

In addition, as described above, in this embodiment, the valve body advancement/retraction rod (4
7) has an automatic adjustment core function, so the distance between the valve seat (44) and the spherical valve element (45), that is, the valve opening degree, can be accurately controlled. In conjunction with the effects of this, more accurate combustion control can be achieved.

[Brief explanation of drawings]

Fig. 1 is a conceptual configuration explanatory diagram of an oil water heater equipped with a variable combustion amount device according to the present invention, Fig. 2 is a cross-sectional side view of a return force spray nostle, Fig. 3 is a control block diagram, and Fig. 4 The figure is a cross-sectional view of the solenoid valve, Figure 5 is an enlarged cross-sectional view of the valve seat of the solenoid valve, Figure 6 is a side view of the pump, Figure 7 is an enlarged cross-sectional view of the shutoff valve, and Figure 8 is Figure 9 is a cross-sectional view taken along line n-■ in Figure 6, Figures 10 to 13 are explanatory diagrams of pressure change curves, and Figures 14 and 15 are solenoid valves. Fig. 16a is an explanatory diagram of the return pressure-closing force straight line;
Fig. 16b is an explanatory diagram of the specification value straight line of the valve spring, Fig. 17 is a cross-sectional front view of the flow rate regulating valve, Fig. 18 is a graph showing the correlation between the applied current and the secondary side pressure of the flow regulating valve, and Fig. 19 The figure is a graph showing the correlation between the secondary side pressure of the flow rate regulating valve, the amount of return oil, and the amount of spray, and FIG. 20 is a conceptual diagram illustrating the configuration of a conventional variable combustion amount device. In the figure: (A) (B) (C) (pc) (G) (N) (S) <p> (R) Combustion amount variable device Petroleum water heater circulation channel flow rate adjustment valve Check valve return type pressure Spray nozzle forward oil pipe Pump return oil pipe (T): (40): (41): (42): (43): (43a) (44): (45): (47): (51): (69): Oil storage tank valve casing Open on one side Open on the other side Flow rate adjustment flow path; Communication flow path Valve seat Spherical valve body Valve body Advance/retreat rod Solenoid Vertical groove for air outflow

Claims (1)

[Scope of Claims] 1) The oil storage tank (T) and the return type pressure spray nozzle (N) are connected to each other through an outgoing oil pipe (S) with a pump (P) installed midway, and the nozzle (N) and outward oil pipe (S
) and the upstream side of the pump (P), and the flow rate adjustment valve (F
The nozzle (N) is connected by a return oil pipe (R) provided with C) and controlled by a flow rate adjustment valve (FC).
In a combustion amount variable device that can change the combustion amount by increasing or decreasing the amount of spray of Oil pipe (R
) is equipped with a solenoid valve (V) having a check valve function, and
A combustion amount variable device characterized in that a hole diameter (D1) of a valve seat (72) of the electromagnetic valve (V) is made larger than a hole diameter (D2) of a valve seat (100) of the shutoff valve (101). 2) The oil storage tank (T) and the return type pressure spray nozzle (N) are connected through an outgoing oil pipe (S) with a pump (P) installed midway, and the nozzle (N) and the outgoing oil pipe (S) are connected in communication.
) and the upstream side of the pump (P), and the flow rate adjustment valve (F
The nozzle (N) is connected by a return oil pipe (R) provided with C) and controlled by a flow rate adjustment valve (FC).
In a combustion amount variable device that can change the combustion amount by increasing or decreasing the amount of spray of Oil pipe (R
) is equipped with a solenoid valve (V) having a check valve function, and
The spring constant of the valve spring (77) that biases the valve body (74) of the solenoid valve (V) in the valve closing direction is
2. The variable combustion amount device according to claim 1, wherein the spring constant of the valve spring (102) is smaller than the spring constant of the valve spring (105) that biases the valve spring in the valve closing direction.