JPS62162315A - Solenoid control device - Google Patents

Abstract

PURPOSE:To accurately position an armature even when there is a small air-gap by a method wherein the titled solenoid control device is constituted in such a manner that the constant of a pressure-opposing spring is changed with the stroke or the position of the armature and that the spring constant is increased when the air-gap between the armature and a magnet core is reduced. CONSTITUTION:The solenoid control device consists of a yoke 1, a magnetic core 2, an excitation coil 3 and an armature 4, and a non-magnetic substance pin 5 is passed through the hole 7 of the yoke 1 and it is pressure-welded to a pressure-opposing spring 8. When a current runs through the coil 3, the armature 4 is attracted in the direction of the core 2, it rotates in counterclockwise direction with a supporting part 9 as the center point. As a result, the pin 5 is shifted downward to bend the spring 8 along the contact supporting face 10 of a base 11, the effective length of the spring 8 is reduced, and the constant of the spring is increased. Accordingly, the armature 4 can be positioned accurately.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a solenoid operating device such as that used in a solenoid valve and/or a pressure regulating valve.

(Prior Art) This type of solenoid operating device is known, for example, from European Patent No. 39000 and German Utility Model No. 7501289.
It is known by the number. In a DC magnet, the attractive force between the core (fixed iron core) and armature (movable iron core) is inversely proportional to approximately the square of the air gap between them. Therefore, if the air gap is small, the linear armature reset spring cannot balance this attractive force, and the armature will move to the position of the smallest possible air gap. On the other hand, if a stronger reset spring is used, the force required to move the armature, and therefore the required current, will be inherently greater, resulting in increased energy consumption and higher temperatures, which are That's not desirable.

(Problems to be Solved by the Invention) It is an object of the present invention to provide a small reset spring that can balance the suction force of the armature even in the case of a small gap, and therefore, in the case of a small gap. Another object of the present invention is to provide a solenoid operating device that allows accurate positioning of a control member moved by an armature. A small reset spring requires only a small current to operate. This object can be achieved by the invention set forth in claim 1 of the present application.

(Means for Solving the Problems) The present invention essentially provides a method in which the spring constant of the spring varies depending on the stroke or position of the armature, that is, the spring constant varies depending on the size of the air gap. The reason for this is that it can be determined in response to changes in the attraction force. Therefore, this spring does not have linear characteristics, but has curved characteristics similar to the curve drawn by the force corresponding to the air gap.

German Utility Model No. 7501289 discloses a solenoid valve in which an armature and a closing member are interlocked by a lever. Here, the center of rotation of the lever is switched to one of two knife edge support points depending on the stroke of the armature. During the first part of the movement, the lever rotates about a first pivot point, and when the movement reaches a predetermined switching position, it engages a second pivot point and remains at this point for subsequent movement of the armature. becomes the new center of rotation. Since such an arrangement uses lever transmission, it requires a relatively large volume and is prone to friction loss.As a result of hysteresis caused by such frictional resistance, accurate positioning of control members, such as valve closing members, is almost impossible. It's impossible. However, in the present invention, the two-stage switching of the spring characteristics can be continuously changed and matched without using any special lever transmission. Preferred embodiments of the invention will be described below.

(Example) As shown in Figure 1, the electromagnetic attraction force F and stroke D of the magnet
Alternatively, the relationship between the core quantity and the air gap is a substantially hyperbolic curve as a result of the fact that this force F is approximately inversely proportional to the square of the air gap. Figure 1 shows l+ >12 >13, respectively.
> Force at different excitation currents I with the relationship of 14 /
It shows a group of curves of stroke characteristics. If this attractive force is opposed by a reset force L of a spring with linear characteristics, that is, a spring with a constant spring constant, the force will be balanced in the range B below the minimum gap D1, as shown in the figure. is not obtained, and the armature is moved in the direction of the smallest possible air gap while the attraction force of the magnet is greater. This smallest possible air gap is usually controlled by a stop. In this way, the armature is prevented from completely contacting and adhering to the core. However, if a reset spring or a pressure counter spring with a curved characteristic R is used, the reset force R is larger than the attractive force F in a small gap, so the intersection of the curve R and one characteristic curve ■ The armature moves away from the core in the direction of , and at this point of intersection the forces are balanced, and in this position the armature becomes stable.

An example of a spring mechanism having the above-mentioned curved characteristics will be explained with reference to FIG. This solenoid operating device has a yoke (yoke) of 1.61 air core and 2. It consists of an excitation coil 3 and an armature 4. The non-magnetic pin 5 extends through a hole 6 in the center of the core 2 and a hole 7 in the leg of the yoke 1, and its tip is in pressure contact with a pressure counter spring 8. The armature can move about the support 9. The spring 8 is a thin plate spring and is in the position shown in the figure when no current is flowing through the coil 3. Here, when a current flows through the coil 3, the armature 4 is attracted toward the core 2 by the magnetic force caused by this current, and therefore the armature 4 rotates counterclockwise around the support portion 9.

This moves pin 5 downwards and bends spring 8. A wedge-shaped or curved contact support surface 1o, which constitutes a part of the base 11, is provided at the lower part of the spring 8. If the force of the armature 4 increases, the spring 8 will be bent downwards and pressed more against the contact support surface 10, with the result that the effective spring length of the pressure counter-spring 8 will be reduced, and thus The stiffness (stiffness) of the spring, that is, the spring constant, increases. This effective spring length is determined by the distance between the contact points of the spring with respect to the contact support surface 10.

The spring in the position shown originally has an effective length that spans its entire length, but when the pin 5 moves downwards, the effective length of the spring is reduced to length C, for example in the position of the spring 8 shown in broken lines in the figure. I am made to do so. As the effective length of the spring decreases, the stiffness of the spring increases. In this way, a spring constant having a desired relationship with the stroke can be obtained, and a curved spring characteristic R can be obtained.

FIG. 3 shows an example in which the solenoid operating device according to the invention is applied to a gas control device having a servo pressure regulator as disclosed in EP 109,978 in terms of its principle and operation. FIG. 3 shows only the parts of this gas control device that are necessary for explaining the present invention. The supply mechanism to the pilot burner and the pilot safety valve are omitted. Components corresponding to those in FIG. 1 of European Patent No. 109978 are given the same number plus 100. The housing is located at 101. Upper portion 102. Intermediate plate 103. cover 104
and a bottom plate 105. The lower part 101 has an inlet 106. Outlet 107 and bulkhead 1 between the inlet and the outlet
Together with the valve seat 109 provided at 08, it forms a control valve housing.

The valve seat 109 cooperates with a closure member 110 of the main valve. This closure member 110 is actuated by a valve stem 111 having a closure spring 113 attached to its head 112. The other end of the closing spring 113 is connected to the guide member 114 of the valve stem 111.
It is fixedly connected to the An intermediate plate 103 connects the yoke 1 of the solenoid operating device to the base 11 and to the cradle. Solenoid operating device is armature 4
, acts on a closing member 118 via a leaf spring 12 connected to this armature and a valve stem 117.

The closure member 118 and the solenoid operating device form a switch-on solenoid valve. A closing spring 121 is held in compression between the valve stem collar 119 and a perforated cover plate 120 for the valve stem 117. When no current flows through coil 3, this closing spring 1
21 connects the closing member 118 to the seat 122 of the solenoid valve.
is pressing against. The inlet pressure at the inlet 106 of the gas control device acts through the passageway 123 to push the closure member 118 further in the closing direction. When a power source (preferably DC) is connected to the coil 3, the armature 4 is connected to the closing spring 1.
The closing member 118 is pushed down and away from the valve seat 122 against the force of 21 and the inlet pressure. This force of armature 4 is transmitted via overtravel spring 12 and valve stem 117. In this way, the inlet pressure is transferred to the passage 12.
3 to a pressure regulator.

The pressure regulator is a diaphragm type pressure regulator.

The diaphragm 125 is part of the integral diaphragm plate 13, which at the same time serves as a sealing device 14 which also serves as a guide for the valve stem 117 passing through the cover plate 120. cover plate 1
The diaphragm chamber 16, which is separated by the diaphragm 125 and the diaphragm 20, has a force transmitting member I7, and when a force is applied, this member 17 acts on the diaphragm 125 via the spring 18 in the following manner. That is, it acts to move the diaphragm 125 and the diaphragm plate fixed to the diaphragm 125 relative to the seat 126 of the bleed valve. This bleed valve communicates through a passage 132 with the control pressure chamber 134 of the operating diaphragm 135 of the main valve 109/110, and on the other hand is connected through a passage 141 with the outlet 107 of the gas control device.

The control pressure chamber 134 of the operating diaphragm for the main valve has an inlet pressure switch-on solenoid valve 118/12.
2, applied via the pressure chamber 138 and throttle 139. Connecting channel 143 connects outlet 107 and pressure chamber 138
is established between. Pressure chamber 138 is separated from population 106 by solenoid valve 118/122, but is connected to control pressure chamber 134 via throttle 139. Connection channel 143 is connected to throttle 144
, which is used as a bleed-off hole to reduce the pressure in the control pressure chamber 134 when the gas control valve is switched off.

The pin 5 is connected to the armature 4 via an adjusting screw 19 and is pressed against a pressure counter-spring 8 . On the opposite side of this spring, as part of the platform 11, a contact support surface 10, which is inclined or curved in shape, is arranged so as to vary the effective length of the spring. The spacer 20 is connected to the spring 8 and the force transmitting member 17
These spacers have wedge-shaped adjustment surfaces that are inclined to each other. The spacer 20 can be moved by the support piece 21 so as to rotate around an axis eccentric to the common axis of the transmission bottle 5 and the force transmission member 17. In this way, the thickness of the spacer inserted between the transmission pin 5 and the force transmission member 17 can be changed, and the distance between them can be changed. This serves, on the one hand, to compensate for manufacturing deviations and, on the other hand, to regulate the minimum gas pressure, ie to determine the lower limit of the adjustment range of the gas control device. The gas flow rate is adjusted by applying varying amounts of current to the coil 3. The higher the current, the more the armature is pushed downwards against the force of the pressure counter-spring 8, and the bottle 5 and the force transmitting member 17 are moved further downwards. An increased force is then exerted on the diaphragm 125 via the spring 18, and as a result, the diaphragm 12 is moved through the passage 141.
The outlet pressure of the control device exerted on the lower side of 5 and necessary to maintain the force balance of diaphragm 125 must be higher than with a small current in coil 3. The main valve 109/110 is The pressure inside control pressure chamber 134 is increased to open wider to obtain the required higher outlet pressure.

As previously explained with reference to FIG. 2, the combination of the pressure counter spring 8 and the contact bearing surface IO results in a desirable characteristic curve of the pressure counter spring, so that even with small air gaps and high excitation currents there is no bleed. The diaphragm 125 that controls the off valve 126 can be stably positioned.

The value of the minimum air gap between the magnetic core 2 and the armature 40 can be adjusted by means of the adjustable contact piece 22. For example, the minimum gap can be increased by moving the contact piece 22 to the right between the core 2 and the armature 4 with respect to the axis of the bottle 5.

This can easily be done by moving the contact piece on a disc, such as an adjustable one, on the core 2 or on the armature.

The operation of this gas control device is essentially
It is similar to that of the gas control device shown in No. 978.

When the inlet pressure increases and the control pressure in the control pressure chamber 134 increases beyond a predetermined set value by the solenoid operating device, this pressure causes the diaphragm 125 to
is lifted from seat 126 and this increment of control pressure bleeds off to outlet 107 via passages 132 and 141.

The force balance is on the one hand pressure chamber 1 below the diaphragm 125.
40 and, on the other hand, by the force applied to the diaphragm 125 by the solenoid operated device. This force can be changed by changing the current value flowing through the coil 3. Spacer 20. The force is transmitted to the upper side of the diaphragm 125 via the force transmission member 17 and the spring 18. If, contrary to the previous case, the pressure on the outlet side rises, the increased pressure will still be present in the passage 14.
1 on the underside of the diaphragm 125, with the result that the diaphragm is again lifted off the valve seat 126 and a portion of the pressure inside the control pressure chamber 134 bleeds off to the outlet, so that the main valve 109/110 The closing spring moves the closing member 110 towards the seat 109 and the gas flow rate decreases.

In other cases, when the pressure at the outlet 107 decreases, the pressure acting on the underside of the diaphragm 135 decreases, so that the control pressure inside the control pressure chamber 134 moves the diaphragm 135 downwardly, opening the main valve 109/110 further. As a result the outlet pressure increases.

The pressure counter-spring 8 and its underlying contact support surface 10 can have various shapes. First of all, this contact support surface does not necessarily have to be flat, but can be curved to obtain the required properties. A thin plate spring is suitable for the pressure counter spring, and as shown in Fig. 4, it has a rectangular shape A, an outer convex shape B, a concave outer shape C5, a circular shape, a trapezoidal shape E, or a shape F in which the slope of the sides of the trapezoid is reversed. It can be in the shape of

The shape of the support base corresponds to the shape of the spring, in particular:
The shape of the inclined support surface IO is selected.

Each spring shape shown in the figures can cooperate with an arcuate or conical contact support surface.

The present invention is not limited to the type of electromagnetic actuator shown in FIGS. 2 and 3. The present invention can be applied not only to a solenoid operating device having a tilting movable armature, but also to a solenoid operating device having a parallel movable armature. Some examples are shown in FIG. A pressure counter-spring which cannot engage the armature or the actuating member as shown in FIGS. 2 and 3 can alternatively be arranged in other positions. Embodiment A in FIG. 5 essentially shows the shape explained in FIGS. 2 and 3. In FIG. In Example B, the force transmitting member 17 is not coaxial with the core 2 but is arranged outside. Examples C, D and E show electromagnetic operating devices having a parallel movable armature instead of a tilt movable armature, where the parallel movable armature is placed inside the coil as in Examples C and D. Alternatively, as in Embodiment E, the core pole piece and yoke can be placed opposite each other. Also, the mechanism for transmitting the movement of the armature 4 or 44 to the closing member of the switch-on type solenoid valve, respectively, will be explained separately. Although not shown in the figure, a number of further methods using transmission means such as levers or springs are possible.The pressure counter-spring can be a V!JFi spring as mentioned above, or the contact support surface can be a flat spring. As mentioned above, a disk spring or a helical spring can be used as long as the effective length of the spring changes depending on the stroke.

(Effects of the Invention) The present invention provides a possibility for a pressure regulator to be operated by a single solenoid operating device not only as an electrically controlled operating device for the pressure regulator but also as a switch-on valve for a servo pressure regulator. is serving. In this way, a substantial simplification is achieved, especially compared to gas control systems which required separate solenoid devices for the two functions. By adjusting the adjustment screw 19 (FIG. 3), the width of the adjustment range, i.e. the difference between the minimum and maximum outlet pressures, can be compensated for, and the operating mechanisms 117, 120 and 118, 122 of the valves can be controlled by the solenoids. The operating mechanism 4, 5.12 of the

[Brief explanation of drawings]

Figure 1 shows curves showing the relationship between the air gap between the armature and core and the attractive force F in a DC electromagnet for different excitation currents, the linear force of the reset spring, and the curve characteristics of the force of the reset spring according to the present invention. It is a figure showing R. FIG. 2 shows an embodiment in which the above-mentioned curved characteristics are obtained by arranging thin plate springs so that the support surface changes with the stroke. Is Fig. 3 a servo-controlled gas system? Figure 2 shows a solenoid operating device according to the invention mounted on a diaphragm pressure regulator forming part of a 711 device. FIG. 4 shows various shapes of reset springs. FIG. 5 shows various arrangements of the magnetic core, armature, reset spring and support. 1... Yoke 2... Magnetic core 3... Excitation coil 4... Armature 5... Pin 8... Pressure counter spring 10... Contact support surface 11... Base 101...・Housing lower part 102...Housing upper part 103...Intermediate plate 105...Bottom plate 110...Closing member 121...Closing spring 118, 122...Solenoid valve part 12...Over Travel spring 13...Diaphragm plate I4...Seal device 16...Diaphragm chamber 18...Spring 125...Diaphragm 126...Bleed valve seat 135...Operating diaphragm 134...Control pressure Room 139.144...Throttle 20...Spacer Patent Applicant Yamatake Honeywell Co., Ltd. Representative Patent Attorney Yoshiharu Matsushita Figure 2 (E) (B) 17, T--'' CD) Figure 5

Claims (2)

[Claims] (1) a magnetic core, a coil surrounding at least a portion of the magnetic core, an armature, an operating member moved by the armature, and a pressure counter spring that engages the armature or the operating member and acts against the magnetic force. A solenoid operating device characterized in that the spring constant of the pressure counter spring changes depending on the actual position of the armature, and the spring constant increases as the air gap between the armature and the magnetic core decreases. (2) The solenoid operating device according to item 1, wherein the pressure counter spring is a thin plate spring.