JP2012219857A - Fluid control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid control valve which includes two valve seats and two valve elements provided in upper and lower portions of a valve stem respectively and controls the flow of fluid by abutting or separating the two valve elements on or from each other, the fluid control valve having high productivity and manufactured inexpensively.SOLUTION: In a gas combustion composite valve, an upper valve seat-abutting part of an upper valve element 25U, at least abutted on an upper valve seat 15U and a lower valve seat-abutting part of a lower valve seat 15L, at least abutted on a lower valve element 25L, are each made of a rubber of predetermined hardness. In the upper valve seat-abutting part, a lower surface 27Ua that is a surface abutted on the upper valve seat 15U is formed in a plane shape. The lower valve seat-abutting part has, at an edge outside the diameter in the radial direction RD orthogonal with the axial direction AX, an abutment deformable part 29L which is protruded in a direction in which a component at a lower side in an axial direction AX and a component at an outside of a diameter in a radial direction RD are combined. The abutment deformable part 29L is elastically deformed and abutted on the lower valve seat 15L.

Description

  The present invention relates to a fluid control valve that controls the flow of fluid by bringing a valve body into contact with or separating from a valve seat. More specifically, the present invention relates to a valve seat seal structure for a fluid control valve in which two valve bodies provided coaxially with each other on one valve shaft are moved in the axial direction so as to abut against the two valve seats to close.

Conventionally, as a fluid control valve for controlling the flow of combustion gas such as propane and city gas, for example, a valve and / or a pressure regulator disclosed in Patent Document 1 and an assembling method thereof can be cited. FIG. 14 shows a valve seat seal structure disclosed in Patent Document 1. FIG. 15 is an enlarged view of a portion E in FIG.
As shown in FIGS. 14 and 15, Patent Document 1 discloses that two upper valve bodies 525 </ b> U provided coaxially on one valve shaft 540 vertically and a lower valve separate from the upper valve body 525 </ b> U. The body 525L is a valve having a valve seat seal structure that moves in the axial direction AX and closes the body by contacting the two upper valve seats 515U and the lower valve seat 515L.

In the lower valve body 525L, a lower elastic plate 527L having a knife edge-like edge portion 529 protruding downward on the outer peripheral edge is attached to the lower valve support member 526L, and in the upper valve body 525U, it is flat on the outer peripheral edge. An upper elastic plate 527U having a simple contact surface is attached to the upper valve support member 526U.
On the other hand, the lower valve seat 515L is formed with a flat contact surface, and the upper valve seat 515U is formed with a knife edge-like edge 519 protruding upward.
In Patent Document 1, when the valve shaft 540 moves downward, the knife edge-like edge portion 529 of the lower elastic plate 527L of the lower valve body 525L is elastically deformed and comes into contact with the lower valve seat 515L. The upper elastic plate 527U of the valve body 525U is elastically deformed and comes into contact with the upper valve seat 515U of the knife edge edge 519 itself to close the valve.

As in Patent Document 1, a valve seat seal structure (hereinafter referred to as “two-stage valve seat seal structure”) in which two valve bodies are brought into contact with each other by moving one valve shaft against two valve seats. ) When a fluid with a large flow rate is controlled by the fluid control valve, the pressure (drag) received on the valve body from the fluid flowing in through the input port and the sealing force of the valve body on the valve seat when the valve body abuts the valve seat There is an advantage that can be reduced.
On the other hand, in the fluid control valve having the two-stage valve seat seal structure, the first valve body contact position first contacting the first valve seat in the first valve body with respect to the axial direction of the valve shaft, and the second valve body In this case, the distance between the valve bodies between the second valve body contact position first contacting the second valve seat and the distance between the valve seats between the first valve seat and the second valve seat must be at least the same.

  However, in the manufacturing process of the body with a valve seat and the parts that make up the valve body, dimensional variations within the dimensional tolerances inevitably occur from product to product. It is possible that a product smaller than the inter-seat distance will be manufactured. If the distance between the valve bodies is smaller than the distance between the valve seats, a gap is generated between the valve body and the valve seat, the valve cannot be completely closed, and fluid leakage occurs.

In the manufacturing process, the valve of Patent Document 1 is located between the lower valve body 525L and the upper valve body 525U in a state where the upper valve body 525U is brought into contact with the upper valve seat 515U downward with a predetermined pressing force. After the lower valve body 525L is brought into contact with the lower valve seat 515L by the biasing force of the arranged coil spring 564, the upper valve body 525U and the lower valve body 525L positioned with respect to the valve shaft 540 are bonded to each other with an adhesive. It is fixed with.
In Patent Document 1, even if the upper valve seat 515U, the lower valve seat 515L, the upper valve body 525U, and the lower valve body 525L have dimensional variations, the upper valve body 525U and the lower valve body 525L are valved. The position fixed to the shaft 540 is dealt with for each product so that the distance between the valve bodies is equal to the distance between the valve seats.

Japanese Patent Publication No.58-131479

However, Patent Document 1 has the following problems.
(1) The problem of low product productivity The upper valve body 525U and the lower valve body 525L must be positioned for each product with respect to the valve shaft 540, resulting in low product productivity and a two-stage valve. It is difficult to manufacture a fluid control valve having a seat seal structure in mass production.
Further, since the upper valve body 525U and the lower valve body 525L are fixed to the valve shaft 540 with an adhesive, it takes time until the adhesive is cured. In addition, in the manufacturing process of the fluid control valve, it is necessary to perform quality control such as the amount of adhesive applied and the adhesive strength, which takes time and effort for process control.

(2) The problem that the product increases in cost Only in order to make the distance between the valve bodies and the distance between the valve seats coincide with each other, an extra part such as the coil spring 564 is required, and the cost of the product increases due to an increase in the number of parts.
In the manufacturing process of the product, since the adhesive is used to fix the upper valve body 525U and the lower valve body 525L to the valve shaft 540, the quality control as described above is performed and the process control is performed. As a result, the cost reflected in the product increases.

  The present invention has been made in order to solve the above-described problems. The two valve bodies provided on the upper and lower sides of one valve shaft are brought into contact with or separated from the two valve seats, respectively. An object of the present invention is to provide a fluid control valve that can control the fluid control valve with a simple structure, high productivity, and low cost.

In order to solve the above problems, the fluid control valve of the present invention has the following configuration.
(1) The first valve seat and the second valve seat are vertically formed, and the first valve body and the second valve body have two valve bodies on one valve shaft, A fluid control valve that moves in the axial direction of the fluid control valve to control the flow of fluid by bringing the first valve body into contact with the first valve seat and the second valve body into contact with or away from the second valve seat. In the first valve body, a first valve seat abutting portion at least abutting on the first valve seat, and a second valve seat abutting portion at least abutting on the second valve seat among the second valve bodies are provided. The first valve seat abutting portion is made of a material having elasticity, and the abutting surface with the first valve seat is formed in a flat shape, and the second valve seat abutting portion is orthogonal to the axial direction. The outer peripheral edge of the radial direction has an abutting deformation part protruding in a direction in which the component on the lower side in the axial direction and the component on the outer side of the radial direction are combined. Valve seat and this Characterized in that it.
(2) In the fluid control valve described in (1), the fluid is a gas.
(3) In the fluid control valve described in (1) or (2), in the closed state, the amount of elastic deformation of the contact surface of the first valve seat contact portion due to contact with the first valve seat is The first crushing amount h1 (0 <h1), and the elastic deformation amount of the contact deformation portion of the second valve seat contact portion due to the contact with the second valve seat is the second crushing amount h2 (0 <h2). The second crushing amount h2 is set to be larger than the first crushing amount h1.
(4) In the fluid control valve according to any one of (1) to (3), the hardness of the second valve seat contact portion is smaller than the hardness of the first valve seat contact portion. Features.
(5) In the fluid control valve described in any one of (1) to (4), the direction of the contact deformation portion is formed at an inclination angle θ = 45 ° with respect to the axial direction. And

The operation and effect of the fluid control valve of the present invention having the above configuration will be described.
In the fluid control valve of the present invention,
(1) The first valve seat and the second valve seat are vertically formed, and the first valve body and the second valve body have two valve bodies on one valve shaft, A fluid control valve that moves in the axial direction of the fluid control valve to control the flow of fluid by bringing the first valve body into contact with the first valve seat and the second valve body into contact with or away from the second valve seat. In the first valve body, a first valve seat abutting portion at least abutting on the first valve seat, and a second valve seat abutting portion at least abutting on the second valve seat among the second valve bodies are provided. The first valve seat abutting portion is made of a material having elasticity, and the abutting surface with the first valve seat is formed in a flat shape, and the second valve seat abutting portion is orthogonal to the axial direction. The outer peripheral edge of the radial direction has an abutting deformation part protruding in a direction in which the component on the lower side in the axial direction and the component on the outer side of the radial direction are combined. Valve seat and this Therefore, in the manufacturing process of the parts such as the body, the first valve body, and the second valve body, the variation in the dimensions within the dimensional tolerance is a product that is the fluid control valve of the present invention (hereinafter simply “product”). However, even if components having such dimensional variations are assembled as they are to constitute the fluid control valve, the first valve body is the first valve seat and the second valve body is the second valve body. The two valve seats can be closed closely without leaking.
Therefore, as described above, the fluid control valve of the present invention is a so-called two-stage valve seat seal in which two valve bodies are brought into contact with each other by moving one valve shaft against two valve seats. Even if it is a structure, it has a simple structure, high productivity, and can be manufactured and provided at low cost.

That is, in a fluid control valve with a so-called two-stage valve seat seal structure, such as the fluid control valve of the present invention, the first valve seat abutting portion of the first valve body has a first contact surface with respect to the axial direction. The inter-valve distance between the first valve body contact position that first contacts the one valve seat and the second valve body contact position that first contacts the second valve seat at the second valve seat contact portion of the second valve body And the distance between the valve seats of the first valve seat and the second valve seat,
L1 ≦ L2 Formula 1
L1: Distance between valve seats (mm), L2: Distance between valve bodies (mm)
Satisfying the above formula 1 is a premise for preventing fluid leakage.

Similar to the conventional valve as disclosed in Patent Document 1, the fluid control valve of the present invention has a dimension within a dimensional tolerance in each component constituting the body, the first valve body, the second valve body, and the like in the manufacturing process. Variations occur for each product, and after assembling each part, the distance between the valve seats and the distance between the valve bodies may be different for each product within the tolerance range of the assembly accuracy, and the above formula 1 may not be satisfied.
In the fluid control valve of the present invention, the product of the fluid control valve is formed so as to always satisfy the relationship of the above formula 1 in consideration of the variation width of the assembly dimension that can occur within the tolerance for each product. Has been.
That is, the second valve seat contact portion of the second valve body is elastically deformed from the position where the contact deformation portion itself starts to contact the second valve seat and contacts the second valve seat. The contact deformation portion of the contact deformation portion is formed with a sufficient margin so that the contact surface of the first valve seat contact portion of the one valve body can contact the first valve seat and be in close contact without leakage.

  Therefore, if the dimensional variation is within the dimensional tolerance for each part constituting the product, the dimensional variation after assembly can be absorbed regardless of the individual product. In the state where the contact surface of the first valve seat contact portion contacts and closely contacts the first valve seat, and the second valve seat contact portion of the second valve body contacts and contacts the second valve seat. The fluid control valve can be closed without leakage.

Further, unlike Patent Document 1, in the fluid control valve of the present invention, in the manufacturing process, the position where the contact surface of the first valve seat contact portion of the first valve body starts to contact the first valve seat; It is not necessary to position the second valve seat at the position where the contact deformation portion of the second valve seat contact portion of the second valve body starts to contact in advance, and the first valve body positioned on the valve shaft and the second valve seat There is no need to fix the two-valve body with an adhesive.
Therefore, the fluid control valve of the present invention can be manufactured as a product in a mass-production system with high productivity, and does not require process management associated with the use of an adhesive that has been required in the past. And man-hours can be reduced. As a result, the fluid control valve of the present invention can be manufactured at low cost.

  Further, in Patent Document 1, an extra part such as a coil spring is attached to the valve only in order to match the distance between the valve bodies and the distance between the valve seats. The fluid control valve of the invention does not require an extra part for matching the distance between the valve bodies and the distance between the valve seats for each product, and is configured with a simple structure, thereby suppressing an increase in the cost of the product.

  Therefore, in the fluid control valve of the present invention, the two first valve bodies and the second valve bodies provided above and below one valve shaft are brought into contact with or in contact with the two first valve seats and the second valve seats, respectively. Even a fluid control valve that controls the flow of fluid by separating it has an excellent effect that it has a simple structure, high productivity, and can be manufactured at low cost.

(2) Since the fluid is a gas, for example, when the flow control of a gas such as a combustion gas having a low pressure and a large flow rate is performed through a large-diameter channel with a small pressure loss, the two first valve bodies, The actuator that controls the flow of gas by bringing the two valve bodies into contact with or apart from each other can be miniaturized. As a result, the entire fluid control valve of the present invention can be made compact.

That is, as in the fluid control valve of the present invention, as a gas, for example, in a combustion gas control valve that controls the flow of combustion gas, the combustion gas is generally circulated at a relatively low pressure of several kPa to several tens of kPa. Is. Therefore, such a combustion gas control valve, for example, has a large flow rate of combustion gas, such as an input port and an output port, and the diameter of the flow path of the combustion gas is about Φ50 (mm) and the flow rate is 40 (m ³ / hour). It is a specification that can be distributed.
On the other hand, downsizing of the combustion gas control valve is required by users. Combustion gas control valve manufacturers are developing a compact combustion gas control valve by reducing the size of the actuator that controls the flow of combustion gas while forming the combustion gas flow path with a large diameter.

In the fluid control valve of the present invention, the two first valve bodies and the second valve bodies are brought into contact with or separated from the two first valve seats and the second valve seats above and below one valve shaft, respectively. To control the flow.
In this fluid control valve, the gas flowing into the input port has a first flow path that is controlled to flow by the first valve seat and the first valve body, and a second flow path that is controlled to flow by the second valve seat and the second valve body. And flow to the output port.
When the first valve body and the second valve body move downward in the axial direction and the fluid control valve closes, the first valve body and the second valve body adjust the pressure of the gas flowing into the valve chamber from the input port. Receive pressure. In other words, the first valve body receives gas pressure from the lower side in the axial direction, while the second valve body receives gas pressure from the upper side in the axial direction.

At this time, the magnitude of the gas pressure received by the first valve body from the gas and the magnitude of the gas pressure received by the second valve body from the gas have the same absolute value. Since the gas pressure on the first valve body side and the gas pressure on the second valve body side are applied in opposite directions, the gas pressure applied to the first valve body and the second valve body is substantially canceled.
Therefore, even if the gas flow controlled by the fluid control valve of the present invention is a large flow rate, the first valve body and the second valve body are not affected by the gas pressure, and the first valve body is connected to the first valve body. The second valve body can be brought into contact with the second valve seat, and the valve can be closed with a relatively small pressing force sufficient to close the seat.

On the other hand, when the fluid control valve of the present invention is opened, a thrust is required to separate the first valve body and the second valve body from the first valve seat and the second valve seat, and this thrust is generated. The actuator to be used only needs to be able to exert only the thrust necessary to overcome the relatively small pressing force when the first valve body is brought into contact with the first valve seat and the second valve body is brought into contact with the second valve seat. .
Therefore, if the thrust exerted becomes small, the actuator can be downsized, and the fluid control valve of the present invention for controlling the gas flow can be made compact.

(3) When the valve is closed, the elastic deformation amount of the contact surface of the first valve seat contact portion due to contact with the first valve seat is a first collapse amount h1 (0 <h1). The amount of elastic deformation of the contact deformation portion of the second valve seat contact portion due to contact with the second valve seat is the second squashed amount h2 (0 <h2), and the second squashed amount h2 is the first squashed amount. Since the amount is set to be larger than the amount h1, the position where the contact deforming portion of the second valve seat contact portion first contacts the second valve seat and then the contact deformation portion starts to contact the second valve seat. From the position where the contact surface of the first valve seat contact portion starts to contact the first valve seat while it is elastically deformed from the first collapse amount to the second collapse amount h2 and is in close contact with the second valve seat, the first collapse amount h1 Until it is elastically deformed and closely contacts the first valve seat.
Therefore, it is possible to seal both the first valve seat and the first valve body and the second valve seat and the second valve body without leakage.

(4) Since the hardness of the second valve seat contact portion is smaller than the hardness of the first valve seat contact portion, the contact deforming portion of the second valve seat contact portion is the first It becomes easier to be elastically deformed than the valve seat abutting portion, the contact area of the abutting deformation portion that abuts the second valve seat can be taken larger, and the first valve seat and the first valve body are brought into close contact with each other By increasing the sealing force between the second valve seat and the second valve body, the valve can be closed more reliably without leakage.

That is, in the fluid control valve of the present invention, when the valve shaft is moved in the direction in which the first valve body and the second valve body are brought into contact with the first valve seat and the second valve seat, the second valve seat contact is first performed. Of these parts, the contact deformation part is mainly elastically deformed. At this time, if the contact deformation part is smaller than the hardness of the first valve seat contact part, the contact deformation part is directed downward in the axial direction. It is easily crushed, and elastically deforms in a state where the contact area with the second valve seat is further increased, thereby closely contacting the second valve seat. Thereby, a certain big sealing force is securable also between a 2nd valve body and a 2nd valve seat.
After that, if the valve shaft further moves in a direction in which the second valve body comes into contact with the second valve seat, if necessary, the first valve body that is about to undergo elastic deformation or is undergoing elastic deformation The first valve seat is in close contact, and a certain large sealing force can be secured between the first valve body and the first valve seat.
Therefore, both the sealing force between the first valve seat and the first valve body and the sealing force between the second valve seat and the second valve body can be increased.

  In addition, it is preferable that especially a contact deformation | transformation part is formed with the hardness corresponded in the range of hardness 50 degrees thru | or 70 degrees in the hardness test by a durometer among 2nd valve-seat contact parts, for example.

(5) Further, since the direction of the contact deformation portion is formed at an inclination angle θ = 45 ° with respect to the axial direction, the dimensions of each part constituting the product are within the dimensional tolerance for each product. Even if it is processed and assembled with variations in range,
Optimum inclination to satisfy both the necessary and sufficient conditions of (a) satisfying the above-described expression 1 and (b) taking a larger contact area with the second valve seat by the elastically deformed contact deformation portion. It becomes a corner.
Therefore, even if the fluid control valve of the present invention has a so-called two-stage valve seat seal structure, the fluid control valve has a high sealing performance when the valve is closed regardless of the dimensional accuracy of each component constituting the product. It can be a control valve.

It is sectional drawing which shows the gas combustion composite valve which concerns on embodiment, and is a figure which shows a valve opening state. It is a figure which shows the valve closing state of the gas combustion composite valve shown in FIG. It is sectional drawing explaining the valve body of the gas combustion composite valve shown in FIG. FIG. 4 is an enlarged view of part A in FIG. 3. FIG. 4 is an enlarged view of a portion B in FIG. 3. In the gas combustion composite valve shown in FIG. 1, it is a figure explaining the relationship between the distance between valve seats, and the distance between valve seats. FIG. 2 is an explanatory diagram showing the flow of combustion gas in the gas combustion composite valve shown in FIG. 1. It is a figure explaining the valve body which concerns on a modification, (a) is sectional drawing which shows a valve body, (b) is an enlarged view of the C section in (a). It is a figure explaining the valve body which concerns on the comparative example 1, (a) is sectional drawing which shows a valve body, (b) is an enlarged view of the D section in (a). It is the graph which contrasted and showed Example 1, 2 and the comparative examples 1 and 2 about the relationship between the load concerning a contact deformation | transformation part, and the amount of sinking. It is an analysis result of the simulation with respect to the lower side valve seat which concerns on Example 1. FIG. It is an analysis result of the simulation with respect to the lower side valve seat concerning Example 2. It is an analysis result of the simulation with respect to the lower side valve seat concerning comparative example 1. It is explanatory drawing of the valve-seat seal structure of the valve disclosed by patent document 1. FIG. It is an enlarged view of the E section in FIG.

(Embodiment)
Hereinafter, embodiments of a fluid control valve according to the present invention will be described in detail with reference to the drawings. Drawing 1 is a sectional view showing the gas combustion compound valve concerning an embodiment, and is a figure showing a valve open state. FIG. 2 is a view showing a closed state of the gas combustion composite valve shown in FIG.
In the embodiment, in FIG. 1, the vertical direction is the axial direction AX, and the horizontal direction is the radial direction RD orthogonal to the axial direction AX. The drawings subsequent to FIG. 2 also follow the directions shown in FIG.

In this embodiment, the fluid control valve is a tandem electromagnetic valve having two fluid control units that control the flow of fluid in parallel with the same structure, as shown in FIGS. 1 and 2. A gas combustion composite valve 1 which is a combustion gas GS such as propane and city gas.
The gas combustion composite valve 1 includes a body 10 in which an upper valve seat 15U (first valve seat) and a lower valve seat 15L (second valve seat) are formed vertically, and an upper valve body 25U (first valve body). As the lower valve body 25L (second valve body), one valve shaft 40 has two valve bodies 25U and 25L. This gas combustion composite valve 1 moves the valve shaft 40 in the axial direction AX of the gas combustion composite valve 1, the upper valve body 25U to the upper valve seat 15U, the lower valve body 25L to the lower valve seat 15L, The flow of the combustion gas GS is controlled by making contact or separation, respectively.

First, the overall configuration of the gas combustion composite valve 1 will be briefly described with reference to FIGS. 1 and 2.
The gas combustion composite valve 1 includes the valve body 20, the valve shaft 40, the core 61, the coil 62, the plunger 63, the urging spring 64, and the guide 65, and the body 10, the support member 66, and the cover 67. Etc.
As shown in FIGS. 1 and 2, the gas combustion composite valve 1 is provided with a core 61 and a plunger 63 coaxially with the valve shaft 40 within the diameter of the coil 62. The coil 62 is electrically connected to a power source (not shown). The plunger 63 is held movably in the axial direction AX by a guide 65 supported by a support member 66 connected to the body 10. The core 61, the coil 62, the plunger 63, the guide 65, and the support member 66 are covered with a cover 67.

The body 10 will be described.
The body 10 is made of metal, and is formed by machining an aluminum die-cast material in the present embodiment. The body 10 has an input port 11 and an output port 12, and a valve chamber 13 is formed between the input port 11 and the output port 12. A filter 18 is provided between the input port 11 and the valve chamber 13 so that foreign matter such as dust mixed in the combustion gas GS flowing from the input port 11 does not flow into the valve chamber 13 by the filter 18. Yes.
In the valve chamber 13, an upper valve seat 15U and a lower valve seat 15L are formed vertically along the axial direction AX on the input port 11 side and the output port 12 side, respectively.

Next, the upper valve seat 15U and the lower valve seat 15L will be described with reference to FIG.
FIG. 6 is a diagram for explaining the relationship between the distance between the valve seats in the body and the distance between the valve seats in the valve body. FIG. 6 intentionally offsets the positions of the body and the valve body in order to make it easier to see the starting point and the end point in the distance between the valve seats and the starting point and the end point in the distance between the valve seats.
As shown in FIG. 6, the upper valve seat 15U protrudes upward and is formed in a convex shape having an R shape near the apex located at the highest part. The upper valve seat 15U and the lower valve seat along the axial direction AX 15L and an annular shape centering on the axial center CL of the valve body 20.

On the other hand, the lower valve seat 15L is planar in the direction along the radial direction RD and is formed in an annular shape centering on the axis CL of the valve body 20.
In the gas combustion composite valve 1, the body 10 is machined by setting the distance between the apex of the upper valve seat 15U and the lower valve seat 15L to a predetermined valve seat distance L1 (0 <L1) with respect to the axial direction AX. Has been.

Next, the valve body 20 will be described with reference to FIGS. 3 to 5.
FIG. 3 is a cross-sectional view illustrating the valve body of the gas combustion composite valve shown in FIG. 4 is an enlarged view of a portion A in FIG. 3, and FIG. 5 is an enlarged view of a portion B in FIG.
In the valve body 20, the upper valve body portion 26U of the upper valve body 25U, the lower valve body portion 26L of the lower valve body 25L, and the connecting portion 21 are made of metal such as aluminum. In the present embodiment, FIG. As shown, the upper valve main body portion 26U and the lower valve main body portion 26L are integrally formed via a connecting portion 21.

The upper valve main body portion 26U has an annular convex portion 26Ut protruding outward in the radial direction RD, and the lower valve main body portion 26L has an annular convex portion 26Lt protruding outward in the radial direction RD. ing.
The upper valve body portion 26U, the lower valve body portion 26L, and the connecting portion 21 have a valve shaft insertion hole 20H along the axial direction AX at the center in the radial direction RD.

The valve body 20 includes at least an upper valve seat 27U (first valve seat contact portion) that contacts at least the upper valve seat 15U of the upper valve body 25U and at least the lower valve seat 15L of the lower valve body 25L. It has a lower valve seat 27L (second valve seat contact portion) in contact therewith.
The upper valve seat 27U and the lower valve seat 27L are made of rubber such as nitrile rubber (NBR), fluorine rubber (FKM, FFKM), ethylene propylene rubber (EPM, EPDM), silicon rubber (Q), etc., and elastic. It consists of the material which has.
The hardness of the lower valve seat 27L is smaller than the hardness of the upper valve seat 27U, and the specific hardness of the lower valve seat 27L will be described in detail later.

  In the upper valve seat 27U, a lower surface 27Ua that is a contact surface with the upper valve seat 15U is formed in a flat shape. When the gas combustion composite valve 1 is closed, the upper valve seat 27U has an elastic deformation amount of the lower surface 27Ua of the upper valve seat 27U due to contact with the upper valve seat 15U before and after the deformation as shown in FIG. Is the first crushing amount h1 (0 <h1).

As shown in FIG. 4, the upper valve seat 27 </ b> U has an outer peripheral surface 27 </ b> Ub and an indented portion 28 </ b> U that is recessed toward the radially outer side in the radial direction RD.
The upper valve body portion 26U and the upper valve seat 27U are firmly fixed as an upper valve body 25U with the convex portion 26Ut and the concave portion 28U being firmly adhered to each other.

The lower valve seat 27L has a contact deformation projecting in a direction in which a component on the lower side of the axial direction AX and a component on the outer side of the radial direction RD are combined on the outer periphery of the radial direction RD perpendicular to the axial direction AX. The contact deformation portion 29L is elastically deformed and comes into contact with the lower valve seat 15L.
Specifically, as shown in FIG. 5, the contact deformation portion 29L is provided at a portion where the lower surface 27La and the outer peripheral surface 27Lb intersect. The contact deformation portion 29L extends in a convex shape with an inclination angle θ = 45 ° with respect to the axis CL of the valve body 20 whose direction is along the axial direction AX, and has the contact deformation portion distal end position 29Lt at the most distal end portion. is doing.

The lower valve seat 27L has an outer peripheral surface 27Lb and a recess 28L that is recessed toward the radially outer side in the radial direction RD.
The lower valve main body portion 26L and the lower valve seat 27L have the convex portion 26Lt and the concave portion 28L firmly adhered to each other, and are integrally fixed as the lower valve body 25L.

In the gas combustion composite valve 1, the valve shaft 40 is inserted into the valve shaft insertion hole 20H by fitting and integrated with the valve body 20, and is fixedly connected to the plunger 63 by screw fastening. The valve body 20 is biased downward in the axial direction AX by a biasing spring 64 disposed between the support member 66 and the upper valve body 26U.
Further, the valve body 20 has a distance L2 between the valve seats L2 (0 <L1 <L2) with respect to the axial direction AX, and the distance between the lower surface 27Ua of the upper valve seat 27U and the contact deformation portion tip position 29Lt of the contact deformation portion 29L. (Distance between valve discs) is set. The height s (0 <s) of the contact deformation portion 29L with respect to the axial direction AX is set to be larger than the difference of (valve seat distance L2−valve seat distance L1).

  When the gas combustion composite valve 1 is closed, the lower valve seat 27L has an elastic deformation amount of the contact deformation portion 29L due to contact with the lower valve seat 15L as shown in FIG. Although it is smaller than the height s of the portion 29L, the size before and after the deformation is the second crushing amount h2 (0 <h2). The second crushing amount h2 is set to be larger than the first crushing amount h1 of the lower surface 27Ua of the upper valve seat 27U.

Next, operation | movement of the gas combustion composite valve 1 is demonstrated using FIG.1, FIG.2 and FIG.7. FIG. 7 is a diagram showing the flow of combustion gas in the gas combustion composite valve.
When the coil 62 is not energized, the valve body 20 is urged to the lower side in the axial direction AX by the urging spring 64, and as shown in FIG. The valve body 25L comes into contact with the lower valve seat 15L, and the gas combustion composite valve 1 is closed.

  On the other hand, when the coil 62 is energized, it is excited to generate a magnetic field in the coil 62 in the axial direction AX, and the core 61 moves the plunger 63 upward in the axial direction AX with a magnetic force that overcomes the biasing force of the biasing spring 64. As a result, the plunger 63, the valve shaft 40, and the valve body 20 rise together as one. Accordingly, the upper valve body 25U that has been in contact with the upper valve seat 15U and the lower valve body 25L that has been in contact with the lower valve seat 15L are simultaneously separated from the upper valve seat 15U and the lower valve seat 15L. Thus, the gas combustion composite valve 1 is opened.

When the gas combustion composite valve 1 is opened, the combustion gas GS flows from the input port 11 to the output port 12 through the valve chamber 13, but the combustion gas GS that has passed through the filter 18 is, as shown in FIG. The flow is divided into the first flow path 13A and the second flow path 13B.
In the first flow path 13A, the combustion gas GS flows to the output port 12 through the space between the upper valve body 25U and the upper valve seat 15U of the opened valve body 20.
In the second flow path 13B, the combustion gas GS passes between the lower valve body 25L and the lower valve seat 15L of the opened valve body 20 and the combustion gas GS flowing through the first flow path 13A and the output port 12 And then discharged from the output port 12.

Next, the lower valve seats according to Examples 1 and 2 and the modification will be described with reference to FIGS. 5 and 8.
FIG. 8 is a view for explaining a valve body according to a modification, in which (a) is a cross-sectional view showing the valve body, and (b) is an enlarged view of a portion C in (a).
In Example 1 and Example 2, the shape of the valve body 20 is common. In the modification, the shapes of the upper valve body 25U and the lower valve body 26L of the lower valve body (second valve body) are the same as those of the first and second embodiments, but the shape of the lower valve seat is the same. Different.

Example 1
As described above, the contact deformation portion 29L according to the present embodiment extends convexly at an inclination angle θ = 45 ° with respect to the axis CL of the valve body 20 whose direction is along the axial direction AX, and is the most distal portion. Has a contact deformation portion tip position 29Lt (see FIG. 5). The hardness of the lower valve seat 27L including the contact deformation portion 29L is 70 ° in a hardness test using a durometer.

(Example 2)
As shown in FIG. 5, the shape of the contact deformation portion 29L according to the present embodiment is the same as that of the contact deformation portion 29L according to the first embodiment. However, the hardness of the contact deformation portion 29L according to the present embodiment is determined by a durometer. The hardness is 60 ° in the hardness test.

(Modification)
In the lower valve body 125L according to this modification, the contact deformation portion 129L of the lower valve seat 127L is inclined at an inclination angle θ = 45 ° with respect to the axis CL of the valve body 20 along the axial direction AX. 8 is formed so as to protrude, and is formed in a shape in which the lower surface 127La and the outer peripheral surface 127Lb are connected by an arcuate surface along a curved line having no inflection point geometrically.
The lower valve body 26L and the lower valve seat 127L are integrally fixed as a lower valve body 125L by fitting the convex portion 26Lt and the concave portion 128L.

Next, the gas combustion composite valve according to Comparative Examples 1 and 2 will be described with reference to FIGS. 6 and 9.
9A and 9B are diagrams for explaining a valve body according to Comparative Example 1. FIG. 9A is a cross-sectional view showing the valve body, and FIG. 9B is an enlarged view of a portion D in FIG.

(Comparative Example 1)
In Comparative Example 1, the shapes of the upper valve body 25U and the lower valve body portion 26L of the lower valve body (second valve body) are the same as those of the first and second embodiments, but the shape of the lower valve seat Is different.
Specifically, in the lower valve body 225L according to the comparative example 1 which is the prior art, the contact deformation portion 229L of the lower valve seat 227L has its direction protruding from the outer peripheral surface 227Lb as it is downward in the axial direction AX. 9 is formed in a shape in which the lower surface 227La and the outer peripheral surface 227Lb are connected to each other at a position away from the lower surface 227La in the axial direction AX. The hardness of the lower valve body 225L is 70 ° in a hardness test using a durometer.
The lower valve body 26L and the lower valve seat 227L are integrally fixed as a lower valve body 225L by fitting the convex portion 26Lt and the concave portion 228L.

(Comparative Example 2)
In FIG. 6 to be referred to, in Example 1 and Example 2, the relationship between the distance L1 between the valve seats and the distance L2 between the valve seats was L1 <L2, but in Comparative Example 2, the distance L1 between the valve seats and the valve seats. This is a case where the relationship with the distance L2 is L1> L2.

Here, the investigation which compared Example 1, 2, and the comparative examples 1 and 2 about the relationship between the load applied to a valve body by valve closing, and the amount of sinking of the lower valve seat of a lower valve body was performed.
The survey conditions are as an example.
(1) Load applied to the valve body: Increased in a range from several (N) to 100 (N).
(2) Distance between valve seats L1: 29.0 (mm) and tolerance width (± 0.05) (mm)
(3) Distance between valve seats L2: 29.05 (mm) and tolerance width (0, +0.2) (mm)
It was.
(4) The investigation was performed on the assumption that the distance difference between the valve seat distance L2 and the valve seat distance L1 was 0.3 (mm).

That is, in the case of the dimensional tolerance illustrated in this way, the body 10 is formed with 28.95 (mm) which is the tolerance lower limit value of the distance L1 between the valve seats, while the valve body 20 is the tolerance of the distance L2 between the valve seats. When the upper limit value is 29.25 (mm), the distance difference between the valve seat distance L2 and the valve seat distance L1 is 0.3 (mm) at the maximum.
In the manufacturing process of manufacturing a plurality of gas combustion composite valves 1, when assembling the parts such as the body 10 and the valve bodies 20, 120 for each product, this maximum distance difference 0.3 (mm) is the valve seat. It may occur between the distance L2 and the distance L1 between the valve seats.

In the gas combustion composite valve 1, when the valve body 20 moves toward the lower side in the axial direction AX, the lower valve seat 27L having the contact deformation portion 29L including the component on the lower side in the axial direction AX is first moved to the lower valve. After contacting the seat 15L, the upper valve seat 27U having a flat lower surface 27Ua contacts the upper valve seat 15U, and the gas combustion composite valve 1 is closed.
Therefore, when the upper valve seat 27U contacts the upper valve seat 15U and the gas combustion composite valve 1 is closed, a maximum distance difference 0.3 (mm) between the valve seat distance L2 and the valve seat distance L1 occurs. In order to satisfy this condition, the amount of depression of the lower valve seat 27L is required to be at least 0.3 (mm).

The survey results are shown in FIG. In Examples 1 and 2 and Comparative Example 1, as can be easily understood from FIG. 10, the upper valve seat 27 </ b> U is brought into contact with the upper valve seat 15 </ b> U in a stage until the sinking amount reaches 0.3 (mm). First, the load that presses the valve bodies 20 and 220 is applied only to the contact deformation portions 29L and 229L of the lower valve seats 27L and 227L.
In Examples 1 and 2, although there is a difference in hardness of the lower valve body 25L at the above stage, there is no difference in an increasing tendency of the sinking amount with an increase in load.
In contrast, the hardness of the lower valve body 225L of the first comparative example is the same as that of the lower valve body 25L of the second embodiment, but the shape of the lower valve body 225L of the first comparative example is that of the first and second embodiments. Since it is different from the shape of the lower valve body 25L, it is difficult to elastically deform as the load increases.

That is, even if the load that presses the valve bodies 20 and 220 is the same, in the first and second embodiments, the contact point between the contact deformation portion tip position 29Lt of the contact deformation portion 29L and the lower valve seat 15L is used as a fulcrum. The bending moment applied at the base of the contact deformation portion 29L in the vicinity of 27La increases.
On the other hand, in Comparative Example 1, the bending moment applied at the base of the contact deformation portion 229L near the lower surface 227La is small with the contact point between the lowermost position of the contact deformation portion 229L and the lower valve seat 15L as a fulcrum.
Therefore, if the load which presses the valve bodies 20 and 220 is the same in Examples 1 and 2, and Comparative Example 1, in the stage until it reaches the sinking amount 0.3 (mm), The sinking amount is larger than that of Comparative Example 1.

On the other hand, when the amount of subsidence exceeds 0.3 (mm), the hardness of the contact deformation portion 29L differs between Example 1 and Example 2 even if the contact deformation portion 29L has the same shape. It can be seen that Example 2, which is lower than Example 1, is easily elastically deformed as the load increases.
Moreover, in Example 1 and Comparative Example 1, as described above, the shape of the lower valve body 25L of Example 1 is the same even if both the contact deformation part 29L and the contact deformation part 229L have a hardness of 70 °. Due to the difference between the shape of the lower valve body 225L of Comparative Example 1 and the increase in load, the tendency of increase in the amount of subsidence differs, and even if the load is the same, Example 1 is more elastically deformed than Comparative Example 1. I understand that.

  On the other hand, in Comparative Example 2 described for reference, when the load that presses the valve body 20 reaches 100 (N), the contact deformation portion 29L of the lower valve seat 27L finally hits the lower valve seat 15L. However, it is not preferable for the actuator to apply a pressing load of 100 (N) to the valve body 20 at this stage.

Next, the amount of displacement that is elastically deformed when a load is applied to the lower valve seat 27L according to Examples 1 and 2 and the lower valve seat 227L according to Comparative Example 1 was analyzed by simulation.
The analysis conditions for the simulation are as follows.
(Common conditions)
(1) In the simulation, the load is applied to a position corresponding to a position where the urging force by the urging spring 64 acts on the upper valve body 26U of the valve body 20 shown in FIGS. 2 and 4 at 0 <F <100 (N The images of the simulation analysis results at the load F = 19.6 (N) are shown in FIG. 11 to FIG. 14 used for later explanation.
(2) The upper valve body 26U, the connecting part 21 and the lower valve body 26L, which are integral, are made of aluminum, have a Young's modulus of 7400 (Kgf / mm ² ), and a Poisson's ratio of 0.34.
(3) The lower valve seat 15L is regarded as a rigid body, and the surface of the lower valve seat 15L has a friction coefficient of 0.1.
(4) The distance L1 between the valve seats and the distance L2 between the valve seats were set to L1 = L2 = 29.05 (mm).

The analysis conditions of the simulation of a different part in each example of Examples 1 and 2 and Comparative Example 1 are shown.
Example 1
In Example 1 above, when the simulation analysis conditions are listed again,
(A) The contact deformation portion 29L extends in a convex shape with an inclination angle θ = 45 ° with respect to the axis CL of the valve body 20 whose direction is along the axial direction AX, and the contact deformation portion tip position is located at the most distal end portion. 29Lt (see FIG. 5).
(B) Hardness of the lower valve seat 27L including the abutting deformation portion 29L: hardness 70 ° in a durometer hardness test

(Example 2)
In Example 2 above, when the analysis conditions for the simulation are listed again,
(C) The shape of the contact deformation portion 29L is the same as that of the first embodiment.
(D) Hardness of lower valve seat 27L including contact deformed portion 29L: hardness 60 ° in a durometer hardness test

(Comparative Example 1)
It is the comparative example 1 and when the analysis conditions for the simulation are listed again,
(E) The contact deformation portion 229L is formed in a shape that protrudes directly from the outer peripheral surface 227Lb to the lower side in the axial direction AX, and has a cross-sectional shape shown in FIG. 9 and is separated from the lower surface 227La to the lower side in the axial direction AX. In this position, the lower surface 227La and the outer peripheral surface 227Lb are connected to each other.
(F) Hardness of lower valve seat 227L including abutting deformation portion 229L: hardness 70 ° in a durometer hardness test

11 to 13 show simulation images as analysis results. FIG. 11 is a simulation analysis result for the lower valve seat according to the first embodiment. FIG. 12 is a simulation analysis result for the lower valve seat according to the second embodiment. FIG. 13 is a simulation analysis result for the lower valve seat according to the first comparative example.
11 to 13, regarding the subsidence amount (displacement amount) of the elastically deformed lower valve seat, the state before the deformation is defined as the displacement amount “0”, and the displacement amount in the deformed state is assigned a minus sign. It is illustrated.

In the first embodiment, as shown in FIG. 11, when the lower valve seat 27L is pressed by the load F, the contact deformed portion 29L, the lower surface 27La, and the outer peripheral surface 27Lb of the lower valve seat 27L are in contact. The vicinity of the base of the deformed portion 29L is mainly elastically deformed locally, and the distribution of the subsidence (displacement amount) is dense. As can be seen from FIG. 11, the largest displacement amount near the base of the contact deformation portion 29L reaches 0.240 (mm). On the other hand, the stroke amount by which the valve body 20 is moved downward in the axial direction AX is also 0.274 (mm), and when the valve body 20 is pressed by the load F, the elastic deformation is almost the contact deformation portion 29L and its root. It can be seen that it is more likely to occur in the vicinity.
This is because the contact deforming portion 29L protrudes in the direction in which the component on the lower side in the axial direction AX and the component on the outer side in the radial direction RD are combined with the peripheral edge on the outer side in the radial direction RD of the lower valve seat 27L. By being formed in a shape, it means that when the valve body 20 is pressed downward in the axial direction AX, it is easily elastically deformed mainly by the contact deformation portion 29L.

On the other hand, in Comparative Example 1, even if the hardness of the lower valve seat 227L is 70 °, which is the same as that of the lower valve seat 27L of Example 1, as shown in FIG. When pressed by a load F, the distribution of the amount of displacement that is elastically deformed by the contact deformation portion 229L is sparse compared to the first embodiment, and the magnitude of the displacement is also about half that of the first embodiment. .
Further, in the lower valve seat 227L, elastic deformation occurs even in the vicinity of the base of the contact deformation portion 229L on the lower surface 227La and the outer peripheral surface 227Lb, or in the range extending from the base to the inner side in the radial direction RD (left side in FIG. 13). However, the largest displacement is 0.180 (mm).
On the other hand, the stroke amount by which the valve body 20 moves downward in the axial direction AX remains at 0.156 (mm). When the valve body 120 is pressed by the load F, the elastic deformation is almost entirely in the entire lower valve seat 227L. As a result, it can be seen that the amount of displacement in the contact deformation portion 229L is smaller than that of the first embodiment.
This is because of the difference in shape between the lower valve seat 227L and the lower valve seat 27L, even when the valve body 220 is pressed downward in the axial direction AX, the contact deformation portion 229L is more elastic than the first embodiment. It means that it is difficult to deform.

  The lower valve seat 27L of Example 2 and the lower valve seat 227L of Comparative Example 3 both have the same hardness of 60 ° and are lower than those of Example 1 and Comparative Example 1 and are pressed by the load F. It is easily elastically deformed.

In the second embodiment, as shown in FIG. 12, when the lower valve seat 27L is pressed by the load F, as in the first embodiment, among the lower valve seat 27L, the contact deformation portion 29L, the lower surface 27La, and The vicinity of the base of the contact deformation portion 29L on the outer peripheral surface 27Lb is mainly elastically deformed locally, and the distribution tends to be dense. As can be seen from FIG. 12, the largest displacement amount near the base of the contact deformation portion 29L reaches 0.30 (mm).
On the other hand, when the valve body 20 is moved to the lower side in the axial direction AX, the stroke amount is 0.332 (mm), and when the valve body 20 is pressed by the load F, the elastic deformation is almost the contact deformation portion 29L and its root. It can be seen that it is more likely to occur in the vicinity.
This is because when the valve body 20 is pressed downward in the axial direction AX, in the first embodiment, the lower valve seat 27L is more elastically deformed by the contact deformation portion 29L than when the lower valve seat 27L is formed with a hardness of 70 °. Means easy.

The operation and effect of the gas combustion composite valve 1 according to this embodiment having the above-described configuration will be described.
(1) In this embodiment, the upper valve seat 15U and the lower valve seat 15L are vertically formed as the body 10, the upper valve body 25U, and the lower valve body 25L. And the valve shaft 40 is moved in the axial direction AX of the gas combustion composite valve 1, the upper valve body 25U is moved to the upper valve seat 15U, and the lower valve body 25L is moved to the lower valve seat 15L. In the gas combustion composite valve 1 that controls the flow of the combustion gas GS by abutting or separating from each other, of the upper valve body 25U, the upper valve seat 27U that is at least in contact with the upper valve seat 15U, and the lower valve body 25L Of these, the lower valve seat 27L at least in contact with the lower valve seat 15L is made of rubber having a predetermined hardness, and the upper valve seat 27U has a flat lower surface 27Ua that is a contact surface with the upper valve seat 15U. Formed, lower valve The seat 27L has an abutting deformation portion 29L projecting in a direction in which a component on the lower side of the axial direction AX and a component on the outer side of the radial direction RD are combined on the outer periphery of the radial direction RD perpendicular to the axial direction AX. Since the contact deformation portion 29L is elastically deformed and comes into contact with the lower valve seat 15L, within the manufacturing process of each part such as the body 10, the upper valve body 25U, the lower valve body 25L, etc. The variation in dimensions occurs for each product (hereinafter simply referred to as “product”) that is the gas combustion composite valve 1 of the present embodiment, and the components having such a dimension variation are assembled as they are. Even when the gas combustion composite valve 1 is configured, the upper valve body 25U can be in close contact with the upper valve seat 15U and the lower valve body 25L can be in close contact with the lower valve seat 15L without leaking.

  Therefore, in the gas combustion composite valve 1 of the present embodiment, the two upper valve bodies 25U and the lower valve body 25L are brought into contact with each other by the movement of one valve shaft 40 with respect to the two upper valve seats 15U and the lower valve seat 15L. Even a so-called two-stage valve seat seal structure in which the valve is closed by contact can be manufactured and provided at a low cost with a simple structure, high productivity.

That is, in a fluid control valve having a so-called two-stage valve seat seal structure such as the gas combustion composite valve 1 of the present embodiment, the upper valve body with respect to the axial direction AX will be described using the gas combustion composite valve 1. The first valve body contact position that first contacts the upper valve seat 15U on the lower surface 27Ua of the 25U upper valve seat 27U, and the lower valve seat 15L at the contact deformation portion 29L of the lower valve seat 27L of the lower valve body 25L. The relationship between the valve seat distance between the first and second valve body contact position (near the contact deformation portion tip position 29Lt) and the valve seat distance between the upper valve seat 15U and the lower valve seat 15L,
L1 ≦ L2 Formula 1
L1: Distance between valve seats (mm), L2: Distance between valve seats (mm)
Satisfying the above formula 1 is a premise for preventing fluid leakage (see FIG. 6).

Similarly to the conventional valve as disclosed in Patent Document 1, the gas combustion composite valve 1 of the present embodiment also has dimensions in the constituent parts such as the body 10, the upper valve body 25U, and the lower valve body 25L in the manufacturing process. Variation in dimensions within the tolerance occurs for each product, and after assembling each part, the distance L1 between the valve seats and the distance L2 between the valve seats differ for each product within the tolerance range of the assembly accuracy. There may be cases where it is not satisfied.
In the gas combustion composite valve 1 of the present embodiment, the relationship of the above formula 1 is considered in consideration of the variation width of the assembly dimension that can occur within the tolerance for each product for the product that is the gas combustion composite valve 1. It is always formed to satisfy.
That is, the lower valve seat 27L of the lower valve body 25L is elastically deformed from the position where the contact deformation portion 29L itself starts to contact the lower valve seat 15L and contacts the lower valve seat 15L. Further, the lower surface 27Ua of the upper valve seat 27U of the upper valve body 25U is formed with a sufficient allowance for the deformation allowance of the contact deformation portion 29L so that the upper valve seat 15U can contact the upper valve seat 15U and be adhered without leakage.

Therefore, if the dimensional variation is within the dimensional tolerance for each part constituting the product, the dimensional variation after assembly can be absorbed regardless of individual products.
Therefore, in the gas combustion composite valve 1 of the present embodiment, the contact deformation portion 29L of the lower valve seat 27L of the lower valve body 25L contacts and comes into close contact with the lower valve seat 15L, and the upper valve of the upper valve body 25U. With the lower surface 27Ua of the seat 27U in contact with and closely contacting the upper valve seat 15U, the valve can be closed without leakage.

Further, unlike the patent document 1, in the gas combustion composite valve 1 of the present embodiment, in the manufacturing process, a position where the lower surface 27Ua of the upper valve seat 27U of the upper valve body 25U starts to contact the lower valve seat 15L; The upper valve body 25U positioned on the valve shaft 40 does not need to be positioned in advance, and the position where the contact deformation portion 29L of the lower valve seat 27L of the lower valve body 25L starts to contact the lower valve seat 15L is not necessary. And the lower valve body 25L need not be fixed with an adhesive.
Therefore, the gas combustion composite valve 1 of the present embodiment can be manufactured as a product in a mass production system with high productivity and eliminates the need for process management associated with the use of an adhesive that has been conventionally required. Time and effort can be reduced. As a result, the gas combustion composite valve 1 of this embodiment can be manufactured at low cost.

  Further, in Patent Document 1, an extra part such as a coil spring 564 is attached to the valve only in order to match the distance between the valve seats and the distance between the valve seats, and the number of parts increases, which is a factor of high cost. The gas combustion composite valve 1 of the present embodiment does not require an extra part for matching the distance L1 between the valve seats and the distance L2 between the valve seats for each product, and is configured with a simple structure, thereby suppressing an increase in product cost. ing.

  Therefore, the gas combustion composite valve 1 of the present embodiment has two upper valve bodies 25U and lower valve bodies 25L above and below one valve shaft 40 with respect to the two upper valve seats 15U and the lower valve seat 15L. Even the fluid control valves that control the flow of the combustion gas GS by contacting or separating from each other have an excellent effect that they can be manufactured with a simple structure, high productivity, and low cost.

(2) Since the fluid is the combustion gas GS, for example, when the flow control of the combustion gas GS with a low pressure and a large flow rate is performed through a large-diameter channel with a small pressure loss, the valve body 20 is brought into contact with or separated from the valve body 20. Thus, the actuator for controlling the flow of the combustion gas GS can be reduced in size, and as a result, the entire gas combustion composite valve 1 can be made compact.

That is, in a combustion gas control valve that controls the flow of combustion gas, such as the gas combustion composite valve 1 of this embodiment, the combustion gas is generally circulated at a relatively low pressure of several kPa to several tens of kPa. is there. Therefore, such a combustion gas control valve, for example, has a large flow rate of combustion gas, such as an input port and an output port, and the diameter of the flow path of the combustion gas is about Φ50 (mm) and the flow rate is 40 (m ³ / hour). It is a specification that can be distributed.
On the other hand, downsizing of the combustion gas control valve is required by users. Combustion gas control valve manufacturers are developing a compact combustion gas control valve by reducing the size of the actuator that controls the flow of combustion gas while forming the combustion gas flow path with a large diameter.

In the gas combustion composite valve 1 of the present embodiment, two upper valve bodies 25U and lower valve bodies 25L (valve bodies 20L) above and below one valve shaft 40 with respect to the two upper valve seats 15U and the lower valve seat 15L. ) Are brought into contact with or separated from each other to control the flow of the combustion gas GS.
In this gas combustion composite valve 1, the combustion gas GS that flows into the input port 11 flows through the first flow path 13A, the lower valve seat 15L, and the lower valve body 25L that are controlled to flow through the upper valve seat 15U and the upper valve body 25U. The flow is divided into two flow paths, the second flow path 13 </ b> B whose flow control is performed, and flows to the output port 12.
When the valve body 20 is urged downward in the axial direction AX by the urging spring 64 and the gas combustion compound valve 1 is closed, the valve body 20 is connected to the input port as shown in FIG. 2 and FIG. 11 receives the pressure of the combustion gas GS flowing from 11 into the valve chamber 13.
In other words, the upper valve body 25U of the valve body 20 receives pressure from the combustion gas GS from the lower side in the axial direction AX, while the lower valve body 25L of the valve body 20 is driven from the combustion gas GS from the upper side in the axial direction AX. Under pressure.

At this time, the magnitude of the combustion gas pressure received by the upper valve body 25U by the combustion gas GS and the magnitude of the combustion gas pressure received by the lower valve body 25L by the combustion gas GS have the same absolute value. Since the combustion gas pressure on the upper valve body 25U and the combustion gas pressure on the lower valve body 25L act in opposite directions, the combustion gas pressure applied to the valve body 20 is substantially canceled.
Therefore, even if the combustion gas GS that is flow-controlled by the gas combustion composite valve 1 has a large flow rate, the valve body 20 is not affected by the combustion gas pressure, and the upper valve body 25U is lowered to the upper valve seat 15U. The side valve body 25L can be closed with only the biasing force of a relatively small biasing spring 64 that is sufficient to bring the side valve body 25L into contact with the lower valve seat 15L.

On the other hand, when the gas combustion composite valve 1 is opened, by energizing the coil 62, the plunger 63 is attracted to the upper side in the axial direction AX with a magnetic force (thrust) that overcomes the biasing force of the biasing spring 64, The plunger 63, the valve shaft 40, and the valve body 20 are raised together.
In order to raise the plunger 63 and open the valve, the thrust required to overcome only the biasing force of the biasing spring 64 which is suppressed to a small value is constituted by the core 61, the coil 62, the plunger 63, the biasing spring 64, and the like. It only has to be demonstrated with an actuator.
Therefore, if the thrust exerted becomes small, the actuator can be downsized, and the gas combustion composite valve 1 that controls the flow of the combustion gas GS can be made compact.

(3) When the valve is closed, the elastic deformation amount of the lower surface 27Ua of the upper valve seat 27U due to contact with the upper valve seat 15U is the first collapse amount h1 (0 <h1), and the lower valve seat The elastic deformation amount of the contact deformation portion 29L of the lower valve seat 27L due to contact with 15L is the second crushed amount h2 (0 <h2), and the second crushed amount h2 is larger than the first crushed amount h1. Since the contact deformation portion 29L of the lower valve seat 27L first contacts the lower valve seat 15L, the contact deformation portion 29L starts from the position where the contact deformation portion 29L starts to contact the lower valve seat 15L. While elastically deforming up to 2 crushing amount h2 and securely contacting the lower valve seat 15L, the lower surface 27Ua of the upper valve seat 27U is elastically deformed from the position where it starts to contact the upper valve seat 15U to the first crushing amount h1. Then, the upper valve seat 15U is securely adhered.
Therefore, it is possible to seal the upper valve seat 15U and the upper valve body 25U, and the lower valve seat 15L and the lower valve body 25L without leakage.

(4) Also, since the hardness of the lower valve seat 27L is smaller than the hardness of the upper valve seat 27U, the contact deformation portion 29L of the lower valve seat 27L is elastically deformed from the upper valve seat 27U. The contact area of the contact deformation portion 29L that comes into contact with the lower valve seat 15L can be increased, and the upper valve seat 15U and the upper valve body 25U are brought into close contact with each other, and the lower valve seat 15L By increasing the sealing force with the lower valve body 25L, the valve can be closed more reliably without leakage.

  That is, in the gas combustion composite valve 1 of the present embodiment, the upper valve body 25U and the lower valve body 25L (valve body 20) are in contact with the upper valve seat 15U and the lower valve seat 15L (on the lower side in the axial direction AX). ), The contact deformation portion 29L of the lower valve seat 27L is mainly elastically deformed. At this time, the contact deformation portion 29L is smaller than the hardness of the upper valve seat 27U. Then, the contact deforming portion 29L is easily crushed toward the lower side in the axial direction AX, and is elastically deformed in a state where the contact area with the lower valve seat 15L is further increased, thereby closely contacting the lower valve seat 15L. Thereby, a certain large sealing force can be secured even between the lower valve body 25L and the lower valve seat 15L.

Thereafter, if the valve shaft 40 further moves in a direction to bring the lower valve body 25L into contact with the lower valve seat 15L as necessary, the upper valve is about to be elastically deformed or is in the middle of elastic deformation. The seat 15U is in close contact with the upper valve seat 15U, and a certain large sealing force can be secured between the upper valve body 25U and the upper valve seat 15U.
Therefore, both the sealing force between the upper valve seat 15U and the upper valve body 25U and the sealing force between the lower valve seat 15L and the lower valve body 25L can be increased.

(5) In addition, since the direction of the contact deformation portion 29L is formed at an inclination angle θ = 45 ° with respect to the axial direction AX, the dimensions of the parts constituting the product that is the gas combustion composite valve 1 are Even if each product is processed and assembled with variation within the range of dimensional tolerance,
Optimum for satisfying both the necessary and sufficient conditions of (a) satisfying the above-mentioned formula 1 and (b) taking a larger contact area to the lower valve seat 15L by the elastically deformed contact deformation portion 29L. The tilt angle is
Therefore, even if the gas combustion composite valve 1 of the present embodiment has a so-called two-stage valve seat seal structure, the sealing performance at the time of closing the valve is not dependent on the dimensional accuracy of each component constituting the individual product. Can be a high fluid control valve.

In the above, the present invention has been described with reference to the embodiments. However, the present invention is not limited to the above-described embodiments, and can be appropriately modified and applied without departing from the gist thereof.
For example, in the lower valve seat 27L of the lower valve body 25L, the contact deformation portion 29L has an inclination angle θ = 45 ° with respect to the axial direction AX, but the inclination angle of the contact deformation portion with respect to the axial direction is For example, it may be less than 45 ° and can be changed as appropriate.

1 Gas combustion combined valve (fluid control valve)
10 Body 15U Upper valve seat (first valve seat)
15L Lower valve seat (second valve seat)
25U Upper valve body (first valve body)
25L Lower valve body (second valve body)
27U Upper valve seat (first valve seat contact part)
27Ua bottom surface (contact surface of first valve seat contact portion)
27L Lower valve seat (second valve seat contact part)
29L Contact deformation part 40 Valve shaft GS Gas (fluid h1 1st crushing amount h2 2nd crushing amount AX Axial direction RD Radial direction

Claims (5)

A first valve seat and a second valve seat are vertically formed, and the first valve body and the second valve body have two valve bodies on one valve shaft, and the valve shaft is connected to the fluid Fluid that moves in the axial direction of the control valve to control the flow of fluid by bringing the first valve body into contact with or separating from the first valve seat and the second valve body against the second valve seat. In the control valve,
Of the first valve body, a first valve seat abutting portion that at least abuts on the first valve seat, and among the second valve body, a second valve seat abutment portion that at least abuts on the second valve seat. And made of elastic material,
In the first valve seat contact portion, the contact surface with the first valve seat is formed in a flat shape,
The second valve seat abutting portion protrudes in a direction in which a component on the lower side in the axial direction and a component on the outer side in the radial direction are combined with a peripheral edge on the radially outer side perpendicular to the axial direction. A fluid control valve having a contact deformation portion, wherein the contact deformation portion is elastically deformed and contacts the second valve seat. The fluid control valve according to claim 1,
The fluid control valve, wherein the fluid is a gas. In the fluid control valve according to claim 1 or 2,
In the closed state, the amount of elastic deformation of the contact surface of the first valve seat contact portion due to contact with the first valve seat is a first collapse amount h1 (0 <h1),
The amount of elastic deformation of the contact deformation portion of the second valve seat contact portion due to contact with the second valve seat is a second collapse amount h2 (0 <h2),
The fluid control valve, wherein the second crushing amount h2 is set to be larger than the first crushing amount h1. In the fluid control valve according to any one of claims 1 to 3,
The fluid control valve according to claim 1, wherein the hardness of the second valve seat contact portion is smaller than the hardness of the first valve seat contact portion. The fluid control valve according to any one of claims 1 to 4,
The fluid control valve according to claim 1, wherein the direction of the contact deformation portion is formed at an inclination angle θ = 45 ° with respect to the axial direction.