JP3365568B2 - Pilot for self-powered control valve - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention
Including large-capacity gas regulators that control supply
Control the pressure or flow rate of various fluids using the control object itself.
Self-powered control valve, especially this self-powered control
Control the valve to a predetermined set pressure according to the pressure fluctuation on the secondary side.
A suitable pilot for a self-powered control valve
You. 2. Description of the Related Art Self-powered control valves are energy
Because the energy is obtained directly from the fluid being controlled,
Although the production volume is limited, the structure is simple and the equipment is relatively
It is easy and convenient if you use it with the best
In recent years, plant construction costs have been reduced, construction time has been reduced, and maintenance costs have been reduced.
It is becoming more and more adopted from the viewpoint of the above. That is, this type of self-powered control valve is controlled
The pressure (or flow rate) of air or gas, which is the control fluid,
Flow from high pressure side (primary pressure P1) to low pressure side (secondary pressure P2)
Direct control of fluid in the middle of the route as a pressure reducing valve system
And the pressure at the low pressure side (secondary pressure P2) (or
Actuator that drives the control valve body according to changes in flow rate)
Used to maintain the secondary pressure P2 at a predetermined set pressure.
Is made up of pilots. This pilot
Is the change in the secondary pressure P2 with the primary pressure P1 of the fluid as the supply pressure
Output the control pressure Px according to
The control valve can be driven. As this type of self-powered control valve, for example,
Used to control the supply of city gas to the secondary side
The schematic configuration of the gas regulator is shown in FIGS.
Is shown. This will be briefly described. In FIG.
Primary side provided in the supply pipe system 2 for gas as a fluid
The amount of supply from the pump to the secondary side is controlled by opening and closing the valve body 3.
The valve body 4 serving as a control valve to be operated is a valve body 3 of the valve body 1.
This is an actuator that is a drive unit for driving
The actuator 4 is slidably provided in the casing 4a.
And is connected to the valve body 3 via a valve rod 5a.
Piston 5 and the valve body 3 of the piston 5 are closed.
And a coil spring 6 for urging in the direction. The one chamber of the actuator 4
(Spring 6 side chamber), from the secondary side of the valve body 1 to the secondary side pressure.
A pilot path 7 for guiding a force (secondary pressure P2) is connected.
On the other hand, the primary side pressure is applied to the other chamber of the actuator 4.
(Primary pressure P1) as supply pressure and according to change in secondary pressure side
10 for self-powered control valve that outputs control pressure Px
Are connected via a control pressure path 8;
Depending on the magnitude of the control pressure Px from the pilot 10, the valve
The body 3 is opened and closed, and the secondary pressure P2 side is
The pressure can be controlled to the set pressure. What
In FIG. 16, reference numeral 9 denotes the primary pressure P
1 is a pilot route for guiding the vehicle. FIG. 17 shows the self-powered control valve shown in FIG.
FIG. 3 is a block diagram corresponding to the entire configuration of FIG.
The same or corresponding parts as in FIG.
The detailed description of is omitted. Here, Fs in the figure is described later.
Set spring force in pilot 10, A is also pyro
Effective area of the diaphragm in the unit 10, K1 is pyro
Pilot gain at unit 10, K2 is actuator
4 is the actuator gain and Gv is the valve valve in the valve body 1.
The body gain, X, is the amount of movement of the valve stem 5a. [0007] In the self-operating control valve system as described above,
FIG. 18 and FIG.
And the configuration shown in FIG.
Was used. This will be briefly described.
Reference numeral 1 denotes a base body formed to have a substantially cylindrical shape.
, 12 and 13 sandwich both sides of the base body 11
With a plurality of mounting bolts 14
Manifold base and sp
In a ring case, these body 11, base 12, body
The first and second dies are provided between the
The diaphragms 15 and 16 are provided therebetween. Reference numeral 17 denotes a position between these diaphragms 15 and 16.
With both diaphragms 15 and 16
Inside the output pressure chamber 18 inside the body 11
A movable stem movably arranged, 19 is a first die;
A predetermined set spring force Fs is applied to the non-movable stem side of the diaphragm 15.
Is disposed in the case 13 so that
The secondary pressure setting spring 20 is connected to the secondary pressure setting spring 19.
To set and adjust the set spring force Fs to an arbitrary value.
Secondary pressure setting adjustment screw. 21 is a case
13 is provided with an adjusting screw 20 which is provided at an upper end thereof.
Spring cover 22 has a secondary pressure setting spring 19 inside.
Partitioned by the first diaphragm 15 in the case 13 provided
This is an atmosphere hole that opens the spring chamber 23 to the atmosphere. Reference numeral 24 denotes a desired set pressure from the output pressure chamber 18.
Of the body 11 to output the control pressure Px for obtaining
The control pressure output ports opened on the sides, 25 and 26
Primary pressure P1, secondary pressure provided on the manifold base 12
P2 is introduced at the introduction port, 27 and 28 are each introduction port.
Introductory passages 29 connected to ports 25 and 26
A second diaphragm 16 at a position 12 facing the second diaphragm 16.
And the secondary pressure P2 is guided through the introduction passage 28.
Is a secondary pressure chamber. Reference numeral 30 denotes a substantially U-shape as a whole, and the one
Nozzle back pressure passage 31 connected to next pressure side introduction passage 27
Is formed at one end of the nozzle member.
The output pressure chamber 18 and the movable
It is disposed through the through hole 17a of the stem 17 and
The end is inserted into the insertion part 12a on the base 12 side and fixed
From the primary pressure introduction port 25 to the passage 31.
The introduction passage 27 is communicated. And
In this nozzle member 30, the nozzle back pressure passage 31 is located at the front.
An air supply nozzle is provided below the through hole 17 a of the movable stem 17.
32 and facing the movable stem 17
A flapper 33 is provided on a part of the
Flapper mechanism is configured. The reference numeral 34 is provided in the movable stem 17 and
The bleed connection between the output pressure chamber 18 and the secondary pressure chamber 29 is performed.
On the road, a fixed throttle 34a is formed in this passage 34 by a small hole.
Is formed. Such a self-powered control valve pilot 10
FIG. 19 shows a schematic diagram of the above-described configuration.
It is. With the conventional pilot 10 having the above configuration,
In order to set the secondary pressure P2 to a predetermined value,
When the adjusting screw 20 is turned, the secondary pressure setting spring 19 is compressed.
The set spring force Fs is applied downward in FIG.
On the lower side of the lower second diaphragm 16
Indicates that the secondary pressure P2 is introduced,
The force Fp due to the received pressure of the effective area A of the
And these are in equilibrium (Fs = Fp = P2 ×
A). The primary pressure P1 is introduced into the air supply nozzle 32.
Out of the slight gap with the flapper 33
A control pressure Px is generated in the pressure chamber 18 and the control pressure Px
Moves the bleed passage 34 from the small hole of the fixed throttle 34a.
Through the secondary pressure chamber 29
You. In such a configuration, the downstream side of the valve body 1
The secondary pressure or flow rate changes, and the secondary pressure P2 becomes
If it has fallen, the upward movement on the second diaphragm 16 side
Force Fp decreases and the movable stem 17 adjusts the secondary pressure
Moving downward with the downward force Fs on the adjusting spring 19 side
become. As a result, the flow of the air supply nozzle 32
The gap with the hopper 33 becomes large, and as a result, the output pressure chamber
The control pressure Px at 18 increases and the actuator 4 side
And the valve body 3 is driven by the actuator 4.
As a result, the valve opening in the valve body 1 increases, and the secondary pressure P2
Is restored, the set pressure is maintained, and the balance returns to the equilibrium state.
Swelling. [0015] By the way, as described above,
The self-powered control valve pilot 10
Is normal in a self-acting pressure reducing valve system.
Although the pressure P1 is on the high pressure side and the secondary pressure P2 is on the low pressure side,
For example, a malfunction occurs in the self-acting pressure reducing valve system
And Px <P2, so-called reverse
There is a possibility that a differential pressure may be generated and adversely affect the diaphragm 16.
there were. That is, the above-described pyroelectric valve for a self-powered control valve.
The two diaphragms 1 used in the unit 10
5 and 16, the displacement of the movable stem 17 is increased.
In order to take off, a corrugated groove is formed, and in the normal state
Is different from the recessed portions in the groove portions of the diaphragms 15 and 16.
Pressure is applied, and the pressure relationship of Px> P2 is maintained.
You. However, as described above, the self-powered decompression
If an abnormality occurs in the valve system, reverse pressure
In some cases, the relationship of Px <P2 may be satisfied.
In the state, the output pressure chamber 18 and the secondary pressure chamber 29 are bleed-connected.
A continuous passage 34 and a fixed throttle 34 formed by a small hole in the middle of the passage 34
The fluid pressure flows backward through a, causing a slight time delay,
Eventually, Px = P2, and then Px> P2
It returned to the normal pressure relationship. In particular, when the system is in an abnormal state as described above,
Further, from the relation of the reverse pressure difference of Px <P2, the output pressure chamber 18
The second diaphragm 16 that defines a space between the second pressure chamber 29 and the second pressure chamber 29
18 is reversed, and upwards in the opposite direction to that in FIG.
Of a convex shape. And the system returns to normal state
When the relationship of Px> P2 is satisfied, the shape returns to the concave shape again.
It was. It should be noted that such an inverse differential pressure Px <P2
The state is, for example, by stopping the supply of the primary pressure P1 side.
Is also caused by an increase in the secondary pressure P2 side.
Was. [0019] Then, in accordance with such a system abnormality, etc.
The reverse differential pressure state where the secondary pressure P2 side becomes high (Px <P
2) occurs, and when the groove of the diaphragm 16 is reversed,
Stress at the bent part near the groove of the diaphragm 16
Deterioration of the diaphragm 16, non-smooth operation,
Hysteresis, etc., and die with more directivity
The damage problem that the diaphragm 16 is torn or torn
Problems with durability and operational reliability
Met. As described above, the output pressure chamber 18 and the secondary
By a small hole provided in the middle of the passage 34 between the pressure chamber 29
The fixed throttle 34a provides stable control of the self-acting pressure reducing valve system.
This is required in terms of performance and response speed.
The cross-sectional area of fluid pressure at
As mentioned above, before returning from Px = P2 to Px> P2
It takes time, and the time of the abnormal state of Px <P2 is long
The problem of becoming inevitable. Further, Px <Px <
When the pressure difference becomes P2, the movable stem 17 rises,
The flapper 33 that constitutes the
The nozzle 32 and the flapper 33 change when they collide strongly.
It leads to shape and damage, and also requires frequent replacement in this regard.
Maintenance issues, such as durability and nozzle flow.
This was a problem in terms of stabilizing the operation of the hopper mechanism. In particular,
These problems are significant when the secondary pressure P2 rises rapidly.
Was something. Further, as described above, the reverse differential pressure of Px <P2
Becomes larger, the system of the self-powered control valve shown in FIG.
In the system, the actuator 4 moves the valve body 3 in the valve closing direction.
Pressurization, resulting in deformation and breakage of the seat surface of the valve seat.
There is also a problem that can eliminate these problems
It is desired to take such measures. Further, the conventional structure as described above
In the case of Ilot 10, one air supply nozzle 32 and this
Due to the flapper 33 on the movable stem 17 side facing the
The control pressure Px is changed only by the slip flapper mechanism
Therefore, the pilot gain K1 is uniquely determined.
The pilot gain K1 (= ΔPx / Δ
P2) is small, and the control pressure P for a change in the secondary pressure P2
x output accuracy (linearity, hysteresis) is poor.
The condition has also occurred. The above-mentioned conventional pilot 10 structure
Since the pilot gain K1 cannot be adjusted,
The entire system including the valve body 1 and actuator 4
Cannot be stabilized, and the pilot gain K1 is small.
Therefore, the control speed of the valve body 1 is slow, and this control system
There was also a problem that the capacity could not be increased at the time. Also, in this type of self-powered control valve system,
Is suitable for initial operation and restarting after maintenance.
Therefore, it is necessary to obtain the valve closed state in the valve body 1 described above.
However, in the pilot 10 structure described above, the primary pressure P1
Side leaks from the air supply nozzle 32 to generate the control pressure Px
Practical problems cannot be avoided, for example, when the set pressure is zero.
(When the spring force Fs of the setting spring 19 is zero)
The control pressure Px is reduced to zero while the air supply nozzle 32 remains open.
The valve body 1 must be fully closed
There is also a problem that can not be
Consideration is also needed. The present invention has been made in view of such circumstances.
And when the self-acting pressure reducing valve system is abnormal, etc.
The control pressure in the output pressure chamber and the secondary pressure in the secondary pressure chamber are reversed,
It is easy and easy to reverse the wavy groove of the diaphragm.
Deformation with a conventional diaphragm etc.
Avoid malfunctions and breakage problems.
Self-reliability that can improve longevity, operational reliability, etc.
The purpose is to obtain an actuator for a force type control valve.
You. Means for Solving the Problems Responding to such a demand
Therefore, the self-powered control valve pilot according to the present invention
And movable stem having second diaphragms at both ends
And a secondary pressure on the non-movable stem side of the first diaphragm.
A force setting spring is provided, and the movable stem is
A first nozzle flapper on the air supply side is provided
Then, primary pressure is introduced to the nozzle of the first nozzle flapper.
Into the second movable diaphragm on the side opposite to the movable stem.
A pressure chamber is formed and exits between the first and second diaphragms.
Pressure chamber, and the output pressure is bled to the secondary pressure chamber.
Pilot for a self-powered control valve
And the movable stem is compatible with the first nozzle flapper.
A second nozzle flange on the exhaust side that performs opening and closing operations
And a communication port for communicating the secondary pressure chamber with the output pressure chamber.
A passage is formed, and a check valve is provided in this passage.
It is. According to the present invention, the self-acting pressure reducing valve system has an abnormality.
Or the supply on the primary pressure side is stopped,
The pressure becomes high on the side, and an inverse differential pressure relationship of Px <P2 occurs.
Even in the middle of the passage communicating between the output pressure chamber and the secondary pressure chamber
Both chambers are brought into the required communication state by the presence of the check valve
This allows the output pressure chamber on the secondary pressure side to be
The fluid flow is obtained smoothly, and the reverse differential pressure condition of Px <P2 is
Smoothly resolved, for inversion with a conventional diaphragm etc.
Low reliability due to deformation, deterioration and malfunction
It causes problems such as lowering, hysteresis, and breakage.
This can be prevented. That is, the check valve
When the condition of Px <P2 is reached, the valve is opened almost simultaneously.
Open until Px = P2. In addition, a normal state having a pressure relationship of Px ≧ P2
In this state, the passage opened at the time of the above-mentioned reverse differential pressure is connected to the check valve.
Therefore, the closed state is maintained, and the self-powered control valve pilot
It is possible to maintain all operating performances. The first on the air supply side
The nozzle flapper and the second nozzle flapper on the exhaust side are
Open / close operation is performed. That is, one nozzle flapper
When the gap moves in the direction that the gap closes, the other
The flapper operates in a direction to open the gap. this
Changes the control pressure output in response to small changes in the secondary pressure
Can increase the pilot gain
Can be. 1 to 5 show a self-operating control valve according to the present invention.
One embodiment of the pilot for
Same or corresponding parts as in FIGS. 16 to 19 described above.
Have the same reference numerals and their detailed description is omitted. Now, according to the present invention, as described above,
First and second diaphragms 15, 16 are provided at both ends.
Of the movable stem 17 and the first diaphragm 15
A secondary pressure setting spring 19 is provided on the moving stem 17 side.
In addition, the air supply side which makes a part of the movable stem 17 a flapper 33
And a first nozzle flapper 40, which is
The primary pressure P1 is introduced into the nozzle 32, and the second diaphragm 1
6, a secondary pressure chamber 29 is formed on the side of the non-movable stem 17,
And an output pressure chamber 18 between the second diaphragms 15 and 16.
The output pressure Px is bleed into the secondary pressure chamber 29.
Pilot for self-powered control valve having passages 34a and 34b
In FIG. 10, it is clear from FIGS.
Thus, a passage communicating the secondary pressure chamber 29 and the output pressure chamber 18
61a and 61b, and
a, equalizing valve 60 is disposed as a check valve in the middle of 61b.
It is characterized by having such a configuration. In this embodiment, the control pressure Px is obtained.
The output pressure chamber 18 and the secondary pressure chamber 2 in which the secondary pressure P2 is introduced.
9 and the base plate 11 and the manifold.
Passages 61b and 61a are provided in the hold base 12
With the base plate 11 and the manifold base 1
Using a connector to connect the passages between
Therefore, the pressure equalizing valve 60 as shown in FIG. 2 is provided as a check valve.
I am. According to such a pressure equalizing valve 60,
Abnormality may occur in the self-acting pressure reducing valve system, or the primary pressure P1
Supply is stopped, the secondary pressure P2 side becomes high pressure
When an inverse differential pressure relationship of Px <P2 occurs, the output pressure
Passages 61a and 61b between the chamber 18 and the secondary pressure chamber 29;
Due to the presence of the pressure equalizing valve 60 provided on the way, both chambers 1
8, 29 can be brought into a required communication state. I
Therefore, the flow of the fluid to the output pressure chamber 18 on the secondary pressure P2 side
, And the reverse differential pressure condition of Px <P2 is quickly eliminated.
Then, the change due to the reversal by the diaphragm 16 or the like as in the prior art.
Deterioration in operation reliability due to shape, deterioration,
It may cause problems such as generation of steresis and breakage.
Can achieve a long life and high reliability.
Things. That is, the pressure equalizing valve 60 is in a state of Px <P2.
In this state, there is no delay as in the past,
The valve is opened almost at the same time until Px = P2
It is configured to keep open. The equalizing valve 6
Actually, the set pressure is set so that the valve is opened and the valve is opened when P2 = Px + α (α is a very small pressure).
It is good to set. In the normal pressure relationship of Px ≧ P2,
In a certain normal state, a passage that is opened at the time of the above-described reverse pressure difference
61a and 61b are closed by the pressure equalizing valve 60.
Maintained, operating performance as a self-powered control valve pilot 10
Can be maintained. Here, the above-mentioned passages 61a, 61b
The cross-sectional area of the flow path at the pressure equalizing valve 60 provided in the
Fixed aperture with small holes in the conventional example or variable aperture 4 described later
9, the output pressure chamber 18 and the secondary pressure chamber 29 are connected.
To optimize system control stability and response speed
So that it is bigger than the passage section
Is set. Further, according to the above configuration, the movable stay
To prevent the nozzle 17 from rising excessively, thereby
The surface of the nozzle 32 and the flapper 33 that constitute the
Can be prevented. Also,
In the configuration described above, the secondary pressure P2 rises rapidly, and this
Assuming that the secondary pressure chamber 29 acts on the diaphragm 16
Can prevent deformation and breakage of the diaphragm surface.
There are also advantages. Further, similar to such a pilot 10,
In the self-acting pressure reducing valve system, the actuator
(Reference numeral 4 in FIG. 16), the reverse differential pressure is applied.
The equalizing valve 60, which is a safety valve in the pilot 10, opens.
Therefore, it is possible to sequentially obtain Px = P2 and Px> P2
To prevent the valve body 3 from being pressurized, and the seat surface and valve seat
It can also prevent the problem of deformation and breakage on the seat surface. Here, the specific structure of the pressure equalizing valve 60 is described.
The structure is explained by the detailed views shown in FIGS. 2 (a) and 2 (b).
For clarity, reference numerals 62a and 62b in the figure denote passages 61a and 61b.
With a diameter (D3, D1) larger than b,
Holes formed in the base plate 12 and the base plate 11
And 63 are slidable in these holes 62a and 62b.
The connector 64 incorporated in the function
The passage 61a on the side of the secondary pressure chamber 29 is urged in the closing direction.
A bias spring having a spring constant Δs, 65 is a hole 62a
Around the passage 61a at the bottom where the passage 61a opens.
A lower O-ring provided with a center diameter dimension D2 to surround it
, 66 communicate with the upper and lower parts in the connector 63
Is a communication passage having a passage diameter d. Note that 6
7 and 67 are seals provided on the outer peripheral portion of the connector 63.
O-ring. That is, the pressure equalizing valve 60 as described above
And the normal pressure relationship Px> P2 or Px = P2
When the force is balanced in the state shown in FIG.
Then, the connector 63 comes into contact with the O-ring 65 and is sealed.
As a result, the passage 61a is closed and the valve is closed.
A variable throttle 49 is provided between the output pressure chamber 18 and the secondary pressure chamber 29.
Only through the connection state, the normal pilot function
Holding. Px · (π / 4) · D2 ^Two + Fs> P2 · (π / 4) · D2 ^Two ‥‥ (1) Here, D2 is the center diameter dimension Fs of the O-ring 65 is the compressive force of the bias spring 64. From this state, P2 rises and Px <P2
Then, the connector 63 moves upward in the figure, thereby
The closed state of the passage 61a is released, and the passages 61a, 61
b, the flow path is fully opened, fluid pressure flows, and Px = P
2 until it reaches 2.
When this is done, the valve is returned to the original closed state. Here, the pressure receiving area of the connector 63
And the upper area A = (π / 4) · D1 ^Two And lower area B =
(Π / 4) D2 ^Two Is equal to the above equation (1)
Is Px · A + Fs> P2 · A, and when Px = P2, the downward direction of the bias spring 64
With the force Fs, the O-ring 65 is sealed and the passages 61a,
61b is closed and blocked. That is, the force of Fs is equal to the force of the O-ring 64.
The opening and closing switching operation point should be set to Px
To make = P2 equal, choose the minimum force of Fs
No. However, at the actual operating point, P2 = Px + α
Where α is equivalent to the force of Fs, and
Since the point can be moved, the spring force can be changed.
With this, it is possible to arbitrarily change the switching operation point.
It is. FIG. 3 shows the flow rate characteristics at the operating point.
In the pressure equalizing valve 60 having the structure shown in FIG.
Draw the characteristics shown. Note that b in the figure is shown in FIG.
This is the characteristic when the adopted structure is adopted. Where the bias
Deviates from Px = P2 by α due to the spring 64, but usually
In some cases, Px ≒ P2, so Px is only α
The pressure equalizing valve 60 opens at a time point lower than P2.
You. Then, this α is set so that the diaphragm 16 is not inverted.
It is understood that the bias spring 64 may be designed each time.
You. It should be noted that in the present embodiment shown in FIGS.
For the pilot 10 for the force type control valve,
Also, the following structure is adopted. That is,
Between the output pressure chamber 18 and the secondary pressure chamber 29 of the movable stem 17
A second nozzle 41 on the exhaust side is provided.
The second flapper 42 advances and retreats toward the second nozzle 41.
A second nozzle which is disposed on the
The first flapper 43 is connected to the first nozzle
It is configured to perform opening and closing operations opposite to the
You. That is, the pie for the self-powered control valve of this embodiment
In the lot 10, the movable stem 17 is supplied with the conventional air supply.
The nozzle 41 on the exhaust side is separate from the nozzle flapper 40 on the exhaust side.
And the flapper 42 facing the exhaust side.
A second nozzle flapper 43 is provided, and the nozzle on the exhaust side is provided.
The nozzle flapper 43 is a nozzle flapper on the air supply side described above.
40 means that one of the gaps Xg1 and Xg2 is
When they open, they work complementarily, like closing the other.
It is configured as follows. By adopting such a configuration,
Output the control pressure Px according to the slight gap change.
You will get. In other words, against a slight change in the secondary pressure P2,
Then, the output of the control pressure Px can be changed. this
Is a pie according to the invention, denoted by a in FIGS.
It will be easily understood from the characteristics of lot 10. In addition, this
In these figures, b is the conventional example shown in FIG.
It shows the characteristic of. In other words, if the above configuration is adopted,
Increase pilot gain K1 (= ΔPx / ΔP2)
17 and thus the block in FIG.
Loop gain Gp = K1 · K of the control system shown in the lock diagram
2. Gv · A can be increased, and as a result
System-wide accuracy (linearity, hysteresis, dead zone)
Etc.) and stabilization and optimization of the entire control system.
There are advantages such as the ability to control the amount. Also, what is indicated by reference numeral 44 in FIG.
Adjusts the gap at each nozzle flapper 40, 43.
Screw it in from the manifold base 12 side
The screw for adjusting the gap,
Therefore, the gap amount Xg (= Xg1 + Xg2) is changed.
Nozzle gain, that is, pilot gay
K1 can be adjusted, and optimal control is selected.
You can choose. That is, in this embodiment, the air supply nozzle
The nozzle 32 and the exhaust nozzle 41 on the axis of the movable stem 17
Arrange them vertically and coaxially with them
By rotating the adjusting screw 44, the exhaust noise is reduced.
The gap amount of the nozzle 41 can be changed to a desired value.
You. In the drawing, reference numeral 45 denotes a lock for locking the adjusting screw 44.
Knut. And for such a gap adjustment
By providing the stitches 44, the gain can be adjusted.
This not only stabilizes the entire control system, but also
Advantages such as prevention of switching and optimization of control speed
Play. 4 and 5, reference numeral 46 denotes the output pressure chamber 18 and the output.
The output pressure passage connecting the power port 24 and 47
The flow of the control pressure Px is provided in a part of the pressure passage 46 so as to be able to advance and retreat.
A first variable for narrowing the passage to vary the amount
The first variable throttle 47 includes a valve body 1 and an actuator.
Adjust the flow rate according to the size of the eta 4
Effective in preventing switching and optimizing control speed.
obtain. In this embodiment, the variable aperture 47 is
Using a screw member screwed into a part of the
However, the present invention is not limited to this. In FIGS. 1 and 5, reference numeral 48 denotes a control pressure Px.
Side output pressure chamber 18 and control pressure output port 24 are bypassed
The connecting bypass path 49 is provided on the way.
The above-described second variable aperture for variably narrowing the path 48
Therefore, control is performed by the bypass path 48 having the variable throttle 49.
To selectively communicate the pressure Px and the secondary pressure P2.
Thus, the diameter of the exhaust nozzle 41 can be changed substantially equivalently.
It works. That is, as described above, the exhaust nozzle 41
By making the chirping diameter d2 adjustable, the supply side and exhaust
The nozzle ratio d1 / d2 can be selected arbitrarily.
Nozzle diameter and pilot gain shown in FIG. 8 as a result of
As is clear from the characteristic diagram showing the relationship between
Air supply is performed based on the nozzle diameter equivalently obtained on the nozzle 41 side.
Make the gain constant or change according to the size of the nozzle diameter
It becomes possible. Here, in FIG.
c, d, and e are ratios of nozzle diameters d1 and d2 on the supply and exhaust sides.
The characteristics when (d1 / d2) is changed are shown.
These nozzle ratios have a relationship of c>d> e. Further, what is indicated by reference numeral 50 in FIG.
Is detachably inserted from the side of the body 11 and stops.
Nozzle rod that is positioned and fixed with female screw 51
The movable stage whose side is movably held in the body 11
Is disposed through the through hole 17a of the
Passage 52 communicating with pilot path 27 on the next pressure P1 side
The passage 52 is formed in the through hole 1 of the movable stem 17.
7a, the air supply nozzle 32 is opened downward.
Are formed. Here, in this embodiment, the nozzle rod 50
Can be easily detached from the outside of the body 11.
The nozzle rod 50 is easily replaced and the air supply nozzle
32 nozzle diameters can be freely selected.
Then, the nozzle rod 50 is replaced in this way to replace the air supply nozzle.
Even when the nozzle diameter d1 of the nozzle 32 is changed, the air supply side and the exhaust
The nozzle ratio d1 / d2 can be arbitrarily selected.
It is clear from the characteristics of c, d, and e in FIG.
As shown, the supply flow rate of the pilot gain K1 and the control pressure Px
Can be made larger or smaller.
Wear the nozzle rod 50 according to the size of the
You only have to remove it and replace it. In particular, such realities
In the example structure, replacement and cleaning of the air supply nozzle 32 can be easily performed.
It has the advantage of being able to do so. In addition, set screw 51
The rod 50 in the body 11
With this, the nozzle flapper 40 on the air supply side is positioned and fixed.
It is for performing the fixed operation. In addition, this nozzle rod 5
The screw hole 50a provided at the outer end of the nozzle rod 5
When replacing 0, screw it in with a screw etc. and hook it.
To use when pulling out with the female thread 51 removed
belongs to. In the present embodiment, the movable stem 17
It has a flapper 33 facing the air supply side nozzle 32
A first mover 53 and an output pressure chamber 18 in the stem 17 are provided.
Of the passages 34a and 34b connecting the pressure chamber and the secondary pressure chamber 29
The exhaust side nozzle 41 communicating with the passage hole 54 constituting
In the passage hole 54.
State biased by the buffer spring 56 in opposite directions
It is provided movably. And with such a configuration,
If the movable stem 17 moves up and down, the air supply side nozzle
32 has a flapper 33 and an exhaust side nozzle 41 has a flapper 4
When each of the movable elements 53 and 55
Since the shock is absorbed by the deflection of the impact spring 56, the conventional structure is used.
The nozzle 32 and the flapper 33 directly collide with each other.
This can reduce the problem of easily causing scratches and the like. Further, 57 in FIG.
The moving stem 17 and the second diaphragm 16
The bias spring 57 is a bias spring that applies an urging force.
Is operated by operating the screw 20 for adjusting the secondary pressure.
Movable when the force Fs by the spring 19 becomes zero.
Push up the stem 17 to raise the nozzle flapper on the air supply side.
40 (32, 33) in the fully closed state, thereby
Control pressure output from output pressure chamber 18 to prevent leakage of P1
This is for setting Px to zero. And like this
When the set pressure is zero, the valve
The body 1 side can be fully closed, and the fluid on the primary side
Leakage can be prevented and this type of self-powered control valve
Appropriate control of the valve body 1 at startup and restart
There are advantages such as doing. In the figure, 59 is the body 11 and the base 12
To connect pilot routes and passages to and from
It is. FIG. 9 shows a pressure equalizing valve characterizing the present invention described above.
60 shows a modification example of FIG. 60, (a) shows normal pressure (Px> P2)
The normal state of the relationship, (b) is the reverse differential pressure (Px <P2)
This shows a state in a relationship. In this embodiment, the connector 63 is held.
The diameters of the holes 62a and 62b are D3 and D1 (D3 <D
The setting is made different from 1), and the connector 63
Is formed in a stepped shape, and as in the case of FIG.
Unlike when there is no area difference between the pressure receiving parts, the area difference between the pressure receiving parts
Is shown. If you do this,
Upper area A ｛= (π / 4) · D1 ^Two ｝ And Connect
Lower area C ｛= (π / 4) · D3 ^Two ｝ Difference
Therefore, an expression similar to the above expression (1)
Then, the following equation is obtained. Px (AC) + Fs> P2 · B (2) where B is the value when the valve is closed by the connector 63 as described above.
Pressure receiving area at the bottom ｛B = (π / 4) · D2 ^Two ｝
You. Then, in the equation (2), the relationship of Px = P2
, The force Fs of the bias spring 64 and the area difference
The connector 63 is pressed against the O-ring 65 by the directional force.
To seal and close the passages 61a and 61b. Here, the sealing force of the O-ring 65 is
Assuming only the downward force due to the area difference of the nectar 63,
The force Fs of the bias spring 64 may be small.
Thus, the spring constant Δs can be minimized. did
Therefore, the amount of deflection of the bias spring 64 can be increased.
Then, the moving amount of the connector 63 at the operating point is increased,
The opening distance E can be increased. In other words, big
The flow from the secondary pressure chamber 29 to the output pressure chamber 18 is obtained at the flow rate Q.
Px = P2 so that Px <P2 is not satisfied.
It can be maintained on the safe side. (In FIG. 3
(See the characteristic indicated by b.) In such a case, Fs is the connector 6
3. The frictional force between the O-rings 67, 67 on the outer periphery and the connector 63
May be the minimum spring constant corresponding to the force obtained by adding the weight of. FIGS. 10 to 13 show the equalizing pressure in the present invention.
9 shows still another modified example of the valve 60. Here, FIG.
0 and the example shown in FIG.
Instead of the O-ring seal,
With a spherical or needle-like (tapered) portion 68
And the opening of the passage 61a is directly opened and closed.
Is shown. Further, in the examples shown in FIGS.
Spherical or needle-shaped part 6 for road opening and closing seal
8 to open the passage 61a in the manifold base 12.
The case where it is formed in the mouth portion is shown. In the figure, 69 is the base
It is a fixed base provided on the 12th side. Of course, in these examples
The structure of FIG. 9 described above, that is, a connector having an area difference
It can be said that it can be adopted for the structure that operates 63.
Needless to say. As shown in FIGS.
As described above, the seal at the equalizing valve 60 is a metal touch.
Self-powered control valve directs line pressure to pilot 10
Therefore, there is a possibility that scale, dust, etc. in the fluid may flow in
As a result, there is little damage to the seal and durability
There is an advantage that it is advantageous in terms of FIGS. 14 and 15 show a self-powered type according to the present invention.
Another embodiment of the control valve pilot 10 is shown and described above.
The same or corresponding parts as those in FIGS.
And a detailed description thereof is omitted. This embodiment differs from the above-described embodiment.
Is a screw for adjusting the air supply nozzle 32 and the exhaust nozzle 41.
44 to the axis of the movable stem 17 formed integrally with
In the direction of intersection,
And the plate-like flappers 70, 71 facing these are
A structure in which the free ends of the leaf springs 72 and 73 are pressed is adopted.
Is Rukoto. And in this state, it's for gap adjustment
When the screw 44 is rotated and adjusted,
One end of the lower exhaust side flapper 71 at the stepped portion 44a
Is pushed upward, so that the other end of the flapper 71
The gap with the exhaust nozzle 41 is changed to a predetermined amount.
What you get. The air supply side nozzle opposing the air supply nozzle 32
One end of the wrapper 70 has a stepped portion above the movable stem 17.
17b, and the movable stem 1
7 to open and close the air supply nozzle 32 in response to the movement of
ing. In this case, the above-described exhaust-side nozzle flapper 4
3 opens and closes the nozzle flapper 40 on the air supply side in reverse.
Swelling. The above-described air supply nozzle 32 and exhaust gas
Nozzle flapper components such as the nozzle 41 are
4 and the nozzle table 74 is divided into two parts.
Sandwiched between the formed bodies 11A and 11B.
Is fixed. In this embodiment, the air supply nozzle 32
Flappers 70 and 7 respectively facing exhaust nozzle 41
1 is opened and closed by swinging about a part as a fulcrum
The buffer spring in the above-described embodiment is
The function of buffering the direct collision of the nozzle flapper
It is not necessary. The self-powered system having the above configuration
The output pressure chamber 18 and the secondary
Passages 61a and 61b communicating with the pressure chamber 29 and the way
A pressure equalizing valve 60 as a check valve provided in the
Functions and effects substantially the same as those of the embodiment shown in FIGS.
Is easily understood. The present invention is limited to the structure of the embodiment described above.
The shape of each part of the pilot 10 for the self-powered control valve,
It goes without saying that the structure and the like can be appropriately modified and changed. For example, in the above-described embodiment, the self-powered control
The secondary pressure setting adjustment by the valve pilot 10 is for setting.
Although the case where the setting is adjusted at the same time 20 is illustrated, the present invention
The secondary pressure setting by the pilot 10 is not limited to this.
May be configured so that settings can be adjusted by remote control.
Of course. In this way, the city gas supply system
Used by time of day, such as nighttime and daytime, such as distribution
If there is a large fluctuation in the volume,
The pressure setpoint at each distribution station where the
Of course, keep it high when working, and keep it low otherwise.
Control the secondary pressure P2 side freely and at the desired value
Things. In the above-described embodiment, the city gas or the like is used.
The present invention is applied to a large-capacity gas regulator that controls the feed rate.
Although the case of applying is exemplified, the present invention is not limited to this.
In addition, various fluids (gas, liquid) can be controlled and fed
The gain will be readily appreciated. As described above, the self-powered type according to the present invention
According to the control valve pilot, the first and second diamonds
A movable stem having flams at both ends, the first die;
A secondary pressure setting spring is provided on the non-movable stem side of the diaphragm
And the air supply side with the movable stem as a flapper
A first nozzle flapper, and the first nozzle
Primary pressure is introduced into the flapper nozzle and the second die
A secondary pressure chamber is formed on the non-movable stem side of the diaphragm,
And an output pressure chamber between the second diaphragm and the second diaphragm.
A passage for bleeding the output pressure into the secondary pressure chamber.
The movable stem,
An opening / closing operation contrary to the first nozzle flapper is performed at the same time.
And a second nozzle flapper on the exhaust side is provided.
A passage connecting the pressure chamber and the output pressure chamber is formed.
Since a check valve is provided in this passage,
In spite of this, various excellent effects listed below are achieved.
I do. That is, an abnormality occurs in the self-acting pressure reducing valve system.
Or the supply on the primary pressure side is stopped,
Has become high pressure, and the reverse differential pressure relationship of Px <P2 has occurred.
Even if the passage between the output pressure chamber and the secondary pressure chamber
Required communication between both chambers due to the presence of a check valve
To the output pressure chamber on the secondary pressure side.
Fluid flow is smoothly obtained, and the reverse differential pressure condition of Px <P2 is obtained.
Resolves quickly and reverses with a conventional diaphragm etc.
Deterioration, reduced reliability in operation, and irregular operation
Preventing the occurrence of hysteresis and further damage,
Long life and high reliability can be achieved. Of course
In a normal state, the passage is kept closed by a check valve,
It can exert the operating performance as a force type control valve pilot
Things. Further, according to the present invention, the movable stem is raised.
To prevent deformation and damage on the nozzle, flapper surface, etc.
Problem can be prevented. Further, a reverse differential pressure is applied to the actuator.
The check valve, which is a safety valve in the pilot,
Obtain Px = P2 and Px> P2 sequentially since the valve opens
To prevent pressurization of the valve body and change the seat surface.
Shape and breakage problems can be prevented. Furthermore,
Opening and closing so that when one opens, the other opens.
The first nozzle flapper and the second nozzle flapper on the exhaust side
The control pressure is output in response to minute changes in the secondary pressure.
Power can be changed and pilot gain can be increased
can do.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partially sectional schematic side view showing an embodiment of a self-powered control valve pilot according to the present invention. FIGS. 2A and 2B show an embodiment of a check valve in the middle of a passage between a secondary pressure chamber and an output pressure chamber which characterizes the present invention. FIG. 2A is an enlarged view of a main part in a normal state, and FIG. It is a principal part enlarged view at the time of a state. FIG. 3 is a characteristic diagram showing control characteristics of pressure and flow rate by a check valve for secondary pressure control, which characterizes the present invention. FIG. 4 is a schematic side sectional view showing an embodiment of the pilot for a self-powered control valve according to the present invention, in which a portion different from FIG. 1 is sectioned. FIG. 5 is a schematic diagram for explaining a fluid circuit of the pilot for the self-powered control valve shown in FIGS. 1 and 4; FIG. 6 is a characteristic diagram showing a gain at an air supply nozzle in a pilot for a self-powered control valve according to the present invention, as compared with a conventional example. FIG. 7 is a characteristic diagram showing a pilot gain of the self-powered control valve pilot according to the present invention in comparison with a conventional example. FIG. 8 is a characteristic diagram illustrating the relationship between the nozzle diameter and the pilot gain in the self-powered control valve pilot according to the present invention. 9A and 9B show a modified example of the check valve for controlling the secondary pressure, which characterizes the present invention. FIG. 9A is an enlarged view of a main part in a normal state, and FIG.
FIG. 3 is an enlarged view of a main part in an abnormal state. FIGS. 10A and 10B show still another modified example of the check valve for controlling the secondary pressure, which characterizes the present invention. FIG. 10A is an enlarged view of a main part in a normal state, and FIG. 10B is a main part in an abnormal state. It is an enlarged view. 11 shows another modification of the check valve for controlling the secondary pressure, which characterizes the present invention. FIG. 11 (a) is an enlarged view of a main part in a normal state,
(B) is an enlarged view of a main part in an abnormal state. FIGS. 12A and 12B show still another modified example of the check valve for controlling the secondary pressure which characterizes the present invention, wherein FIG. 12A is an enlarged view of a main part in a normal state, and FIG. It is an enlarged view. 13A and 13B show still another modified example of the check valve for controlling the secondary pressure, which characterizes the present invention, wherein FIG. 13A is an enlarged view of a main part in a normal state, and FIG. 13B is a main part in an abnormal state. It is an enlarged view. FIG. 14 is a schematic side sectional view showing another embodiment of the self-powered control valve pilot according to the present invention. FIG. 15 is a schematic diagram for explaining a fluid circuit of the pilot for the self-powered control valve shown in FIG. 14; FIG. 16 is a schematic configuration diagram for describing a schematic configuration of a gas regulator that is a self-powered control valve including a valve body, an actuator, and a pilot. FIG. 17 is a block diagram of the self-powered control valve of FIG. 16; FIG. 18 is a schematic sectional view of a conventional self-powered control valve pilot. FIG. 19 is a schematic view for explaining a pilot fluid circuit in FIG. 18; [Description of Signs] 1 Valve body 2 Gas supply piping system (controlled fluid supply piping system) 3 Valve element 4 Actuator 5 Piston 7 Secondary pressure side pilot path 8 Control pressure path 9 Primary pressure side pilot path 10 Pilot (self-powered type) Pilot for control valve) 11 Base body 12 Manifold base 13 Spring case 15 First diaphragm 16 Second diaphragm 17 Movable stem 18 Output pressure chamber (set pressure output chamber) 19 Spring for setting secondary pressure (for setting secondary pressure) Spring) 20 Secondary pressure setting adjustment screw (Secondary pressure setting adjustment screw) 21 Spring cover 22 Atmospheric hole 23 Spring chamber 24 Control pressure output port 25 Primary pressure introduction port 26 Secondary pressure introduction port 27 Primary pressure introduction passage 28 Secondary pressure introduction passage 29 Secondary pressure chamber (secondary pressure chamber) 30 Nozzle member 31 Nozzle back pressure passage 32 Air supply nozzle 33 33 Flapper 34 Passage 40 between output pressure chamber and secondary pressure chamber 40 First nozzle flapper 41 Second nozzle 42 Second flapper 43 Second nozzle flapper 44 Gap adjusting screw 46 Output pressure passage 47 First variable throttle 48 bypass path 49 second variable throttle 50 nozzle rod 56 buffer spring 57 bias spring 60 equalizing valve (check valve) 61 (61a, 61b) passage 62a, 62b hole 63 connector 64 bias spring 65 O-ring 66 communication passage 68 Metal touch seal part (spherical or needle-shaped part) 69 Fixed base 70 Flapper 71 Flapper 72 Leaf spring 73 Leaf spring

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Eiji Tagaya 4-13-23 Nakameguro, Meguro-ku, Tokyo Tokyo Gas Apartment 417 (72) Inventor Toshihiro Hara 3-24-8 Bessho, Urawa-shi, Saitama ( 72) Inventor Takanari Maruyama 19-18, Sakurada-cho, Atsuta-ku, Nagoya-shi, Aichi Prefecture Inside Toho Gas Co., Ltd. Inventor Yoshihiro Tsuruoka 4-1-1, Omagari, Samukawa-cho, Koza-gun, Kanagawa Prefecture Inside the Shonan Plant (72) Inventor Koji Nakahashi 4-1-1, Omagari, Samukawa-cho, Koza-gun, Kanagawa Shonan Plant (56) References JP-A-64-70805 (JP, A) JP-A-60-41109 (JP, A) JP-A-3-30107 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) G05D 16/00-16/20

Claims (1)

(57) Claims 1. A movable stem having first and second diaphragms at both ends, and a secondary pressure setting spring provided on a side opposite to the movable stem of the first diaphragm. A first nozzle flapper serving as an air supply side using the movable stem as a flapper, and introducing a primary pressure to the nozzle of the first nozzle flapper , A self-powered control having a secondary pressure chamber formed on the non-movable stem side of the diaphragm, an output pressure chamber between the first and second diaphragms, and a passage for bleeding the output pressure to the secondary pressure chamber; In the valve pilot, the movable stem is opposed to the first nozzle flapper.
The second nozzle flapper on the exhaust side for opening and closing
A self-powered control valve pilot , wherein a passage for communicating the secondary pressure chamber and the output pressure chamber is formed, and a check valve is disposed in the passage.