JPS6018701Y2 - Solenoid flow control valve - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an electromagnetic flow control valve configured to control pressure on the fluid outlet side using electromagnetic force.

FIG. 1 shows the structure of a conventional flow control valve of this type.

In the figure, 1 is the valve body, 2 is a primary chamber provided with a fluid port 2a connected to a fluid inflow pipe (not shown), 3 is a valve seat formed on the inner wall of the valve body 1, and 4 is a fluid passage inside the valve body 1. The valve body is interposed in the valve body so that it can come into contact with the valve seat 3.

5 is a permanent magnet fixedly attached to the upper end of the valve body 4 via a fixing plate 6, and 7 is a diaphragm whose center portion is held between the valve body 4 and the fixing plate 6 and whose peripheral portion is supported by the wall portion of the valve body 1. and supports the valve body 4.

A secondary chamber 8 is provided with a fluid outlet 8a connected to a fluid outflow pipe (not shown), and can communicate with the primary chamber 2 via the valve body 4.

9 is a communication port for communicating the upper space partitioned from the primary chamber 2 with the atmosphere by the diaphragm 7; 10 is an outer magnetic pole fixed to the valve body 1; and 11 is a central part of the outer magnetic pole 10 facing the permanent magnet 5. A fixed core 12 is provided as a fixed core 11.
13 is an electromagnetic coil wound around the winding frame 12.

To explain the operation of the flow control valve having such a configuration, when the electromagnetic coil 13 is energized to a predetermined value, the fixed iron core 11 and the outer magnetic pole 1
0, a magnetic circuit is formed, and an electromagnetic repulsive force Fr commensurate with the amount of current applied to the permanent magnet 5 acts in the direction of the arrow in FIG. 1 to push down the valve body 4.

On the other hand, the fluid forced into the primary chamber 2 through the fluid flow 2a exerts a force Fl on the valve body 4 and a force F2 on the diaphragm 7 in the direction of the arrow in the figure, and the valve body 4 and the valve seat 3 are further pushed down. The fluid passes through the gap formed by the fluid, flows into the secondary chamber 8, and is ejected through the fluid outlet 8a to an outflow pipe (not shown) at a pressure corresponding to the pressure in the secondary chamber B (secondary pressure).

At this time, a force F3 corresponding to the above pressure acts on the valve body 4 as shown by the arrow.

In this case, each force F□, F2. F3. Fr balance and each pressure P1. P2 (Added in Figure 1) Also, the effective area AD of the diaphragm (shown in Figure 1) and the valve seat area AV
The relationship (shown in FIG. 1) is as shown in the following equation.

First, the pressure P1 of the fluid flowing in from the inlet 2a causes a pressure loss at the opening between the valve body 4 and the valve seat 3, and becomes F2.

The force F1 that pushes the valve body downward in the figure is the valve seat area AV.
and the value F2 multiplied by Pl = AVxP, ... (1) The force F2 that pushes the diaphragm upward in the figure is the value F2 multiplied by the effective area of the diaphragm and Pl = Oil x P,
...(2) Also, the force F3 that pushes the valve body upward is the value F2 multiplied by the area AV of the valve seat F = AVxP2 - (31 The valve when Fl, F2, F3. and Fr are balanced Due to the pressure loss corresponding to the opening area between the body and the valve seat, the fluid that flows in at the inlet pressure P1 becomes the pressure P2 at the time of discharge, so (1), (2), (Equation 31 and F
The relationship between r is as shown in the following equation.

Fr10F□=p2,000F3 + f
(4) In the above equation, f is the fluid force that acts when the fluid flows through the proportional valve.

f is extremely small compared to other terms of value and can be ignored in reality.

Now, by setting fΣ0 in equation (4), (1), (2),
(Substituting formula 31, Fr 0 AvxP1 = ADxP1 + AvxP2 ---
(5) When this is rearranged with respect to F2, it becomes as follows.

p2=K V-AI 5... (6) V This equation shows the basic characteristics of this proportional valve, and AVI
If designed like an IAD, equation (6) can be simplified as shown in the following equation.

Fr P, = i − (7) In this formula, Pl
is not included, AV is a constant value, and F2 is F
It is a function only of r.

That is, if Fr=constant, P2=constant, and F2 is P
It is a constant value regardless of □.

In other words, it has the function of a governor.

Furthermore, if Fr is changed, F2 changes in direct proportion to Fr.

F2 is the pressure of the fluid discharged through the outflow pipe (not shown), and has a relationship with the discharge amount as shown in the following equation.

Q: Discharge flow rate Q=-A-, /P2 K: Proportionality constant A: Discharge tube open area If Fr is changed and F2 is controlled, the discharge flow rate can be controlled.

Therefore, by controlling the amount of current applied to the electromagnetic coil 13, the amount of fluid ejected can be controlled.

However, when the fluid to be controlled is fuel gas, there are various gases in both pressure and flow rate.

For example, in the case of commercially available LPG, the supply pressure Pt = 28
0WH20 is the standard, whereas the discharge pressure P2 is 2
There are cases where you want to set it to about 50mmH, 0, and in the case of general city gas, the supply pressure P = 100mm
The pressure of H201 discharge pressure P2=5orH1H20 is a common ratio.

According to the results of tests conducted by the inventors of the present application, P2 of the above LPG is 250 within the range of commonly used fuel gas.
When obtaining a pressure such as mH2O, Fr in equation (7) above becomes the maximum value, and the design dimension d of the electromagnet's magnetic circuit
, D1. It was found that unless D29g, h, etc. were selected strictly, the desired pressure could not be reached.

The present invention was developed in view of the above points, and permanent magnets,
It is an object of the present invention to provide a compact flow control valve that can improve the efficiency of electromagnetic repulsion and can be put to practical use by selecting one configuration of a fixed core and an outer magnetic pole, and their mutual positional relationship.

That is, the present invention has a valve body interposed in a fluid passageway and supported by a diaphragm, a permanent magnet integrally attached to the valve body, and a permanent magnet provided inside an outer magnetic pole facing the permanent magnet. It has a fixed iron core and is equipped with an electromagnetic coil that generates a maximum force in the direction of repelling the permanent magnet when energized, and the valve opening is controlled by the balance between the electromagnetic repulsion force and the fluid pressure acting on the diaphragm and valve body. In the electromagnetic flow control valve, the outer diameter of the tip of the fixed iron core on the side facing the permanent magnet is d1, the outer diameter of the permanent magnet is Dl, the hole diameter of the opening formed on the side of the outer magnetic pole facing the permanent magnet is D2, and the outside diameter is D1. When the distance between the opening surface of the magnetic pole and the end face of the fixed core facing the permanent magnet is 1, and the minimum gap between the fixed core and the permanent magnet is g, d/D□=0.5 to 0.9D2/ Ds=1.1-1.
5゜h≦t/20e 1/2 (D2-Dz)>9
It is configured to satisfy the condition v.

Therefore, by setting these conditions, if the fixed iron core, outer magnetic pole, and permanent magnet are configured and arranged so as to satisfy the above-mentioned conditions, the efficiency of the electromagnetic repulsive force against the permanent magnet can be improved, and the efficiency of the electromagnetic repulsion force against the permanent magnet can be improved, and it is larger than the conventional one for the same magnetomotive force. You can obtain electromagnetic repulsion.

Hereinafter, one embodiment of the present invention will be described based on the drawings.

FIG. 2 is a model of the shapes and mutual positional relationships of the fixed iron core, outer magnetic pole, and permanent magnet of the flow control valve according to this embodiment.

In the figure, 15 is a permanent magnet that can move up and down integrally with the valve body (not shown), 16 is an outer magnetic pole with a circular opening 16a formed in the center of the wall surface on the side that is fixed to the valve body, and 17 is a permanent magnet that can move up and down as in the conventional case. A fixed iron core is provided in the outer magnetic pole 16 , and one end face is fixed to a substantially central core of the upper wall of the outer magnetic pole 16 , and the other end face faces the permanent magnet 15 .

Then, the outer diameter of the permanent magnet 15 is Dl, the thickness is t1, the hole diameter of the opening 16a formed in the outer magnetic pole 16 is D2, and the fixed iron core 1
The outer diameter of the tip facing the permanent magnet 15 of No. 7 is d1, and the minimum gap between the permanent magnet 15 and the fixed iron core 17 is g1. When the distance from the end face of the magnet 17 facing the permanent magnet is h, the shapes and mutual positional relationships thereof are configured to satisfy the following conditions.

1 d/D□=0.5~0.95 2 D2/D1 = 1-1~1.5 Gong≦t/2+9 4 1/2 (D2 DI)>9 Next, these conditions and the electromagnetic repulsion force Fr The relationships are shown in FIGS. 3 to 5.

Figure 3 shows the outer diameter d of the end of the fixed iron core and the outer diameter D1 of the permanent magnet.
This figure shows the relationship between the ratio of and the electromagnetic repulsive force Fr under a constant magnetomotive force.

The magnetomotive force is expressed by N and I, where N is the number of turns of the electromagnetic coil and I is the current flowing through the coil.

From the figure, it can be seen that the electromagnetic repulsive force Fr shows a maximum when d/DI is around 0.75, and the repulsive force Fr acts effectively when d/D1 is in the range of 0.5 to 0.95.

FIG. 4 shows the relationship between the ratio of the hole diameter D2 of the opening of the outer magnetic pole to the outer diameter D□ of the permanent magnet and the electromagnetic repulsion force Fr under a constant magnetomotive force, and D2/DI is about 1.1 to 1. It can be seen that within the range of 5, the electromagnetic repulsive force Fr acts effectively.

That is, when D2/D1 becomes smaller than 1.1, the outer magnetic pole 16
The attractive force between the permanent magnet 15 and the permanent magnet 15 becomes remarkable, and the electromagnetic repulsion force Fr
If D2/Dt becomes larger than 1.5, the electromagnetic repulsion force Fr itself becomes weaker.

FIG. 5 shows the axis that acts on the permanent magnet 15 and the outer magnetic pole 16 when the upper end surface of the permanent magnet 15 is changed from 0 to t (thickness of the permanent magnet 15) with respect to the two surfaces of the outer magnetic pole 16. Indicates directional repulsive and attractive forces.

In the figure, when the middle part of the thickness of the permanent magnet 15 is on the above two sides, the force acting between the permanent magnet 15 and the outer magnetic pole 16 becomes zero, and if the permanent magnet 15 shifts from this position to either side, it returns to its original state. A magnetic force F acts to return it to its position.

It can also be seen that when either end of the permanent magnet 15 is at the position of the two surfaces, the magnetic force F tends to be zero.

From this, in order to effectively utilize the electromagnetic repulsive force Fr, the value of X in FIG. 2 may be set within the range of 0 to t/2.

As mentioned above, as is clear from Figures 3 to 5, the above-mentioned 1)
By configuring and arranging the fixed core, the outer magnetic pole, and the permanent magnets so as to satisfy the conditions of ~4), the efficiency of the electromagnetic repulsion force against the permanent magnet 15 can be improved, and a larger electromagnetic repulsion force can be obtained than the conventional one with the same magnetomotive force. I can do it.

FIG. 6 shows a comparison of the relationship between the electromagnetic repulsion force Fr acting on the permanent magnet and the magnetomotive force between a conventional control valve and that of the present invention. In the figure, curve A is for the present invention, and curve B is for the present invention. shows the conventional one, and it can be seen that there is a significant difference.

As a result, the number of turns of the electromagnetic coil has been reduced to approximately 17 compared to the conventional method.
2. It is possible to reduce the winding resistance to about 1n, and the flow control valve can be made compact.

In the present invention, the valve part is a primary pressure control type governor, but it is also possible to use a valve part structure that has a function such that the reaction force acting on the diaphragm is approximately constant within a predetermined primary pressure fluctuation range of the control valve. Needless to say, it's good as long as it lasts.

As described above, according to the present invention, the efficiency of the electromagnetic repulsive force against the permanent magnet is extremely high, and as a result, the number of windings of the electromagnetic coil can be reduced, making it possible to make the control valve more compact than before. It is possible to configure a flow control valve with a size within a practical range, which was previously difficult.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional view explaining the structure of a conventional electromagnetic flow control valve, FIG. Figure 3 shows the relationship between the ratio of the diameters of the fixed iron core and the permanent magnet and the electromagnetic repulsion force, and Figure 4 shows the relationship between the ratio of the diameters of the permanent magnet and the hole provided in the outer magnetic pole and the electromagnetic repulsion force. Figure 5 is a diagram showing the relationship between the position of the permanent magnet and the magnetic force acting between the permanent magnet and the outer magnetic pole at that time, and Figure 6 is a diagram showing the relationship between the position of the permanent magnet and the magnetic force acting between the permanent magnet and the outer magnetic pole. It is a diagram comparing repulsion forces. 1... Valve body, 4... Valve body, 7...
...Diaphragm, 13...Electromagnetic coil, 1
5...Permanent magnet, 16...Outer magnetic pole, 1
6a...Opening, 17...Fixed iron core.

Claims (1)

[Claims for Utility Model Registration] A valve body interposed in a fluid passage and supported by a diaphragm, a permanent magnet integrally attached to the valve body, and a permanent magnet provided inside an outer magnetic pole. Equipped with an electromagnetic coil that has fixed iron cores facing each other and generates magnetic force in a direction that repels the permanent magnet when energized, the valve opening is determined by the balance between the electromagnetic repulsion force and the fluid pressure acting on the diaphragm and valve body. In the electromagnetic flow control valve, the outer diameter of the permanent magnet is D□,
The hole diameter of the opening formed on the side facing the permanent magnet of the outer magnetic pole is D2.
, when the distance between the opening surface of the outer magnetic pole and the end surface of the fixed core facing the permanent magnet is h, and the minimum gap between the fixed core and the permanent magnet is g, d/D = 0.5 to 0.9D2 /D□=1.1~1.
5゜h≦t/2+9.172 (D2-Dl)>da. An electromagnetic flow control valve characterized by being configured to satisfy the following conditions.