KR20100122585A - Valve operating mechanism using differential pressure - Google Patents

Abstract

PURPOSE: A valve operating mechanism using differential pressure is provided to minimize the load by decreasing the area exposed to the pressure chamber of a piston by expanding the diameter of a support. CONSTITUTION: A valve operating mechanism using differential pressure comprises a pressure chamber(21), a guide(22), a piston(51), and a valve support member(50). The fluid is filled in the pressure chamber. The guide is formed on the central axis of the pressure chamber. The piston is held in the pressure chamber and lifts with respect to a valve sheet by the differential pressure between the fluid and other fluid, which is filled in the expanded part of the inlet-side flow channel. The valve support member comprises a support(52), which is protruded from the center of the piston and is inserted into the guide, attaches and supports the valve(60) to the bottom of the piston. The exposed area to the pressure chamber of the piston is narrower than that to the expanded part(14) of the inlet-side flow channel.

Description

VALVE OPERATING MECHANISM USING DIFFERENTIAL PRESSURE

The present invention relates to a valve operation mechanism using a differential pressure, and in detail, a method for minimizing the load on the valve member in a structure in which the valve member is moved by the differential pressure of the fluid acting on both sides to open and close the flow path. will be.

The valve that controls the flow or flow of the fluid is subject to a significant load on the pressure difference on both sides of the inlet and outlet of the fluid, and the load increases with the control flow rate. Since the operation of the valve requires more force than the load, it is not possible to directly operate the large flow control valve with a large load.

It is well known to use differential pressure to operate a large load control valve without difficulty. The valve using the differential pressure is to open and close the main channel by moving the main valve by the difference between the inlet side pressure of the main channel and the internal pressure of the pressure operating chamber by installing a pressure chamber that can trap and control the fluid separately from the main channel. The pressure chamber is connected to the inlet side of the main flow path through a fine orifice and also to the outlet side flow path through the pilot flow path. The pilot flow passage is larger than the orifice and has a much smaller aperture than the main flow passage and is opened and closed by a separate small auxiliary valve (also called a pilot valve). In other words, by operating the small auxiliary valve to control the internal pressure of the pressure chamber, the main valve is operated by using the difference between the internal pressure of the pressure chamber and the inlet pressure of the main flow path, and therefore, It is possible to operate the flow control valve.

As an example of such a differential pressure valve operation mechanism, Korean Patent Registration No. 10-0532974, 10-0734743, etc. propose a structure using a diaphragm valve as a main valve. The valve member of the diaphragm-type valve opens and closes the flow path by exposing its one side edge to the inlet side of the main flow path and all of its other sides to the pressure working chamber to expand and contract by the differential pressure on both sides thereof.

Patent Document 10-2004-0092430 proposes a structure using a piston-attached valve as a main valve. In the piston type valve, the annular valve member is attached to the piston member, and the piston member is installed in the cylinder-type pressure acting chamber so that one side edge thereof is exposed to the inlet side of the main flow path and all the other side of the pressure acting chamber is installed. And the valve member is moved by linear reciprocation by the differential pressure on both sides thereof.

In a valve using a differential pressure, a load corresponding to the pressure difference of the fluid acting on both sides of the valve member acts. To reduce this load, it is necessary to reduce the difference in the area where the fluid on each side contacts the valve.

However, in the conventional diaphragm type or piston type type, the one side of the valve member or the supporting member is exposed to the inlet side passage except for the diameter of the valve seat, and the other side thereof is completely exposed to the pressure chamber. Therefore, at least the difference in the diameter of the valve seat, that is, the area of the cross-sectional area of the main flow path exists, and the differential pressure according to the difference in the area acts as a load at all times.

Therefore, in the large flow rate control valve using the differential pressure, the load increases according to the flow rate, and the valve member is opened and closed in a state in which the pressure applied to both sides is disturbed, so that a momentary large impact is applied to the valve seat when the valve is opened and closed. There is a problem that the valve member is easily worn or damaged.

The valve member in the diaphragm type described above is generally made of a general rubber material because it requires flexibility corresponding to the stretching motion. General rubber material is very suitable as a valve member because of its flexibility, low cost, and good adhesion, but its life is generally short because it is less durable against load.

The valve member in the aforementioned piston attachment type can be replaced with a durable Viton or Teflon material instead of the general rubber material, but the price is expensive. In particular, the valve member needs to be pressurized with a greater force because the adhesion is inferior to that of the general rubber material. In this case, the valve body forming the pressure chamber with the piston member is also very uneconomical because it must be made of metal with high strength.

In addition, if the load of the valve is large, the flow rate of the pressure chamber must be largely controlled in order to exert a force exceeding the load, and thus the control performance is lowered such as the opening / closing speed of the valve is lowered. In addition, the auxiliary valve must be large according to the control flow rate of the pressure chamber and the operation time becomes long, which is disadvantageous in miniaturization and low power consumption.

An object of the present invention is to provide a valve operation mechanism using differential pressure to minimize the load by improving the structure to narrow the exposed area of the main valve to the pressure chamber in the valve using the differential pressure.

A valve operation mechanism using the differential pressure according to the present invention for achieving the above object, wherein the fluid inlet side flow path is expanded around the valve seat of the valve member, and the fluid flows through another flow path at a position facing the expansion portion of the inlet side flow path. Forming a pressure acting chamber into which the pressure chamber can be filled, forming a guide section partitioned into a separate space coaxial with the pressure acting chamber, and receiving the pressure of the fluid contained in the pressure acting chamber and filled therein, A flange-shaped piston part which is exposed to the expansion part and receives the pressure of the fluid filled therein and is raised and lowered with respect to the valve seat by the differential pressures on both sides thereof, and a support part which protrudes from the center of the piston part and is inserted and lifted into the guide part. And a valve support member attached to and supporting the valve member under the piston part.

Preferably, in order to increase the degree of freedom of design to minimize the load, the guide portion is formed to protrude outward from the center of the pressure acting chamber so that the guide space can be further expanded if necessary.

In addition, the diameter of the guide portion and the support portion inserted therein is preferably increased so that the valve support member is elastically pressed against the valve seat in the guide portion instead of weakening the working pressure from the pressure chamber than the inlet side flow path side. A spring is inserted to compensate for the differential pressure required for the valve operation to operate the valve member.

According to the present invention, the valve support member is exposed to the inlet side flow path where one side of the piston portion is extended around the valve seat so that the pressure of the fluid filled therein acts and the other side is exposed to the pressure action chamber and filled therein. When the pressure of the fluid acts, the pressure is raised and lowered in the direction of opening and closing the valve member with respect to the valve seat by the differential pressure on both sides thereof.

A feature of the present invention is that the piston portion has a flange shape with a support portion at the center thereof. The flange-shaped piston part can be designed in different areas depending on the diameter of the support part. That is, when the diameter of the support portion is increased, the area exposed to the pressure action chamber of the piston portion decreases by that much. Therefore, it is possible to design to minimize the load.

As a preferred aspect of the present invention, the guide portion into which the support portion of the valve support member is inserted may be formed in a shape projecting outward on its central axis without being disposed inside the pressure action chamber, which is used to increase the support portion. Increase design freedom. For example, instead of making the exposed area of the piston part to the pressure chamber smaller than the exposed area to the inlet side of the main flow passage, the insufficient force of the differential pressure necessary for the valve operation can be compensated with a spring, which makes the valve member a large moment with respect to the valve seat. It can pressurize smoothly without any impact.

As described above, the present invention is effective in minimizing the load and extending the life of the valve. Thus, using a valve member made of general rubber material reduces the price increase factor due to the valve member, and in particular, there is no durability burden on the load, so Since the valve body can be manufactured, for example, as a synthetic resin mold, it is possible to reduce the price and mass production of the valve, thereby contributing to the cost reduction of the valve.

The present invention is also effective in miniaturization of the valve since the operation means for operating the valve, for example, the solenoid mechanism, can be further miniaturized by minimizing the load.

The present invention is also effective in reducing the power consumption of the solenoid mechanism while improving the performance of the valve by increasing the response characteristics of the valve by reducing the load.

As an embodiment of the valve operation mechanism using the differential pressure according to the present invention, an electromagnetic pilot valve using the same is illustrated in the drawings. Examples of the drawings are intended to help the understanding of the present invention to the last, and may differ from actual ones, such as being exaggerated or omitted for each main part.

The electromagnetic pilot valve as illustrated in the figure is composed of the main valve body 10, the pilot valve body 20 and the solenoid mechanism 30, which is interposed between the main valve body 10 and the pilot valve body 20 A main valve member 40, a valve support member 50 for supporting the main valve member 40, and a pilot valve member 60 interposed between the pilot valve body 20 and the solenoid mechanism 30. . The main valve body 10 and the pilot valve body 20 can be made of a synthetic resin injection molding according to the present invention, it may be of a structure that can be screwed together or fastened by a separate bolt element.

The main valve body 10 forms a main flow path leading to an inlet flow passage 11, a valve seat 12 of the main valve member 40, and an outlet flow passage 13 for entering and exiting a fluid such as water, The flow path expansion part 14 which extended the inlet side flow path 11 around the valve seat 12 is provided.

The pilot valve body 20 is provided as a space protruding outward from the center of the pressure acting chamber 21 and the pressure acting chamber 21 at a position facing the flow path expansion portion 14 of the main valve body 10. It has a guide portion 22 that is, and accommodates the valve support member 50 of the main valve member 40 there. The pressure action chamber 21 communicates with the flow path expansion portion 14 of the main valve body 10 through a fine orifice 53 penetrating the valve support member 50. The pressure acting chamber 21 is also connected via a pilot flow path 23, a valve seat 24 of the pilot valve member 60, a pilot outlet hole 25, and a connection hole 56 of the valve support member 50. It communicates with the outlet side flow path 13 of the valve body 10. Here, the pilot flow path 23, the pilot outlet hole 25, and the connection hole 56 from the orifice 53 flow a fluid to the pressure operating chamber 21 as a different flow path from the main flow path. The pilot flow path 23 and the subsequent flow paths are formed larger than the orifice 53 and much smaller than the aforementioned main flow path.

The solenoid mechanism 30 is a conventional one, and the solenoid coil 31, the plunger 32 which wanders in response to the electronic thrust by the exciting current of the solenoid coil 31, and the spring 33 for the return of this plunger 32 are Although not shown in detail, it may include a permanent magnet for latching the plunger 32 against the return spring 33. The plunger 32 is operated to attach and support the pilot valve member 60 to the end thereof so that the plunger 32 emerges and is held in the opening and closing direction with respect to the valve seat 24.

The valve support member 50 of the main valve member 40 is composed of a flange-shaped piston portion 51 accommodated in the pressure acting chamber 21 described above, and a support portion 52 inserted into the guide portion 22 described above. The main valve member 40 is attached and supported under the piston 51. Here, the area of the upper surface of the piston portion 51 exposed to the pressure chamber 21 is designed to be slightly larger than the area of the lower surface exposed to the flow path expansion portion 14 of the inlet side flow path, and the ratio is the guide portion. The diameter of the support 22 and the support 52 inserted therein may vary.

The sealing members 55 and 56 enclosed around the piston part 51 and the support part 52 slide in close contact with the wall surface of the pressure-acting chamber 21 and the wall surface of the guide part 22, and the fluid is formed in the gap with each wall surface. To prevent leakage. The spring 57 has elasticity to push the valve support member 50 toward the valve seat 12, and is weaker than the pressure acting on the piston portion 51 from the fluid filled in the inlet side flow path of the main flow passage, It is provided to ensure the safe return operation of the valve support member 50 and the closed state of the main valve member 40 after the return operation, it is not necessary.

In the example in the figure, the guide portion 22 is formed outside the pressure operation chamber 21 in order to increase the design freedom with respect to the diameter of the support portion 52 of the valve support member 50. For example, the diameter of the support part 52 is made larger so that the area of the piston part 51 exposed to the pressure acting chamber 21 is made smaller than the area exposed to the flow path expansion part 14, and the spring 57 The strength can be slightly increased to compensate for the differential pressure required to operate the valve. Thus, the spring 57 is always elastic, thereby avoiding the impact of the main valve member 40 on the valve seat 12 caused by the sudden flow rate fluctuation of the pressure chamber 21, and smooth opening and closing.

Hereinafter, the operation of the electromagnetic pilot valve as described above. 1 shows a state in which the valve is closed, and FIG. 2 shows a state in which the valve is open. The shaded portions in the figures depict the flow of fluid.

In the initial state in which the main valve member 40 and the pilot valve member 50 are all closed as shown in FIG. 1, the pressure chamber of the internal pressure P1 of the inlet side flow path 11 of the main valve body 10 and the pilot valve body 20 is provided. (21) The internal pressures P2 are equal to each other (P1 = P2). However, since the upper surface of the piston portion 51 of the valve support member 50 is slightly wider than the lower surface thereof, the force for pressing the upper surface having a large area to the same pressure is higher than the force for pressing the lower surface. Therefore, the valve support member 50 is forced downward, and the main valve member 40 is pressed against the valve seat 12 and maintained in its closed state.

When the plunger 32 is pulled upward in the drawing by the electronic thrust of the solenoid coil 31 by operating the solenoid mechanism 30 in the state as shown in FIG. 1, the pilot valve member attached to the plunger 32 ( 60 opens the valve seat 24. Then, the fluid filled in the pressure chamber 21 passes through the pilot flow path 23, the valve seat 24 opened and the pilot outlet hole 25 and through the connection hole 54 of the valve support member 50. It flows out to the outlet side flow path 13 of the main valve body 10. As a result, the internal pressure P2 of the pressure acting chamber 21 decreases and becomes lower than the internal pressure P1 of the inlet flow path 11 (P2 <P1), so that a pressure difference occurs between each other. In this case, the piston portion of the valve support member 50 ( 51) The force to press the lower surface is much stronger than the force to press the upper surface. Therefore, the main valve member 40 opens the valve seat 12 on the main flow path, thereby bringing it to the state of FIG. This state continues while the pilot valve member 60 is pulled by the solenoid mechanism 30.

In the state of FIG. 2, when the plunger 32 is returned by operating the solenoid mechanism 30, the valve seat 24 is again blocked by the pilot valve member 60, from which the pressure action chamber 21 is opened. Newly filled with the fluid flowing through the orifice 53 from the inlet side flow path 11 of the flow path, the internal pressure P1 of the inlet flow path 11 and the internal pressure P2 of the pressure operating chamber 21 are equal again (P1 = P2), and thus the valve seat 40 is closed by the main valve member 50 in the state of FIG.

The present invention is not limited to the above described and illustrated in the drawings. For example, the main valve member attached to the flange-shaped piston portion according to the present invention may be a diaphragm type, for example, a known shape other than that illustrated in the drawings. In addition, since the solenoid mechanism is provided to control the valve by an electric signal, it may be removed in the case of manual operation and a manual operation button may be installed instead.

1 is a cross-sectional view showing a closed state of the electromagnetic pilot valve to which the valve operation mechanism using the differential pressure according to the present invention is applied.

Figure 2 is a cross-sectional view showing an open state of the electromagnetic pilot valve to which the valve operation mechanism using the differential pressure according to the present invention.

Explanation of symbols on the main parts of the drawings

10: main valve body

14: Euro extension

20: pilot valve body

21: pressure chamber

22: guide

40: main valve member

50: valve support member

51: piston part

52: support

60: pilot valve member

Claims (3)

The inlet flow passage of the fluid extends around the valve seat of the valve member and is formed at a position facing the expansion portion of the inlet flow passage so that the fluid can be filled through another flow passage. A guide part partitioned in the flange portion, a flange-shaped piston part which is raised and lowered with respect to the valve seat by a differential pressure of a fluid contained in the pressure action chamber and a fluid filled therein and an expansion part of the inlet-side flow path and a central part of the piston part. A valve operating mechanism using differential pressure, characterized in that the valve is provided with a support for protruding from the guide portion is inserted and lifted guided by the guide portion and attached to the valve member under the piston. The method according to claim 1, wherein the exposed area to the pressure action chamber of the piston portion is smaller than the exposed area to the expanded portion of the inlet-side flow path, and is provided with a spring that is received in the guide portion to press the valve support member, A valve operation mechanism using differential pressure, characterized in that the spring retains elasticity that compensates for a force corresponding to the area difference between both sides of the piston. The valve operation mechanism using differential pressure according to claim 1 or 2, wherein the guide portion is formed to protrude outward on a central axis of the pressure action chamber.

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