JP2000161529A - Automatic adjusting valve device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain an economical and automatic adjusting valve device with a high performance in which a design, manufacturing, maintenance control are easy, a cost is low and a fluid pressure is controlled automatically and surely and a chattering and hunting are hard to occur and the block by a foreign articles is hard to occur. SOLUTION: In this automatic adjusting valve device for throttle and controlling a passage by perceiving the state change of fluid a first automatic adjusting valve device V and a second automatic adjusting valve device V' are installed in a row in the passage and also an orifice 41 is provided in the passage and by perceiving the reduction of the front/rear pressure difference of the orifice when a passing flow rate becomes small, a pressure difference pilot device Q for closing the first automatic adjusting valve device V prior to the second automatic adjusting valve device V' is provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic adjusting valve device such as a constant pressure valve, a constant flow valve, and a liquid level control valve which senses a change in the state of a fluid and controls the throttle of a flow path. In the present specification, the term “water” generically represents a fluid.

[0002]

2. Description of the Related Art Conventionally, various types of automatic regulating valve devices such as a constant pressure valve, a constant flow valve, and a liquid level control valve for controlling a flow path by sensing a change in a fluid state have been proposed.
In particular, a method is known in which a pilot valve is used to control the opening and closing of the main valve by increasing or decreasing the internal pressure of a main valve driving pressure chamber that drives a larger-diameter main valve. A typical configuration of the main valve device M is shown in FIG.
Are driven in conjunction with the opening and closing of the pilot valve device P. In the main valve device M, the main valve having a main valve seat 4 in the inlet flow path a, the outlet flow path c, and the communication flow path thereof A main valve body 5 and a main valve driving member 6 having a pressure receiving area larger than the main valve body 5 are provided inside a box 1 via a main valve shaft 7 so as to be able to advance and retreat. The main body 5 forms a throttle flow path with the main valve seat 4, and the main valve driving member 6 is slidably fitted to the cylindrical wall 3 of the main valve box. A main valve driving pressure chamber d is formed between the main valve driving pressure chamber d and the pilot valve device P. The main valve driving pressure chamber d is closed when the downstream pressure of the main valve is higher than a predetermined value, and is opened when the downstream pressure is lower than the predetermined value. The driving pressure chamber d is communicated with the inlet flow path a on the upstream side of the main valve via the throttle control valve 10 and the outlet on the downstream side of the main valve via the pilot valve device P. It communicates with the road c.

In the pilot valve device P, the pressure receiving plate 2
A pressure chamber i into which the downstream pressure of the main valve is introduced is formed on one of the sides, and an urging member 28 as a predetermined pressure means is mounted on the other side. Valve element 23 which is operated by the balance of opposing force with the means
Opens and closes the pilot flow path. With this configuration, when the downstream pressure of the main valve becomes lower than a predetermined value,
The pilot valve device P is opened, the internal pressure of the main valve driving pressure chamber d decreases toward the downstream side of the main valve, and the main valve body 5 is driven by the thrust caused by the difference in the pressure receiving area between the main valve body 5 and the main valve driving member 6. 5, when the downstream pressure of the main valve becomes higher than a predetermined value, the pilot valve device P is closed, and the internal pressure of the main valve driving pressure chamber d is increased. The pressure rises toward the upstream pressure, the main valve element 5 closes, the supply liquid is restricted, and the downstream pressure of the main valve is kept constant.

[0004]

However, these automatic regulating valve devices according to the prior art have a structure in which the supply of liquid is restricted by the opening and closing movement of only the main valve element 5 having a size corresponding to the diameter of the liquid supply line. is there. Therefore, when the flow rate is small, the main valve body 5 is operated in a state very close to the main valve seat 4. In addition to the main valve body 5, the flow near the main valve body 5 becomes a high-speed flow in which the pressure pulsation is likely to occur. It tends to cause so-called "chattering" or "hunting" that generates sound or vibration, and as a result, the durability of the main valve body 5 or the main valve seat 4 is reduced, and there is also a possibility that a water hammer may be induced. There was a problem.

Accordingly, the present invention provides a simple and clear principle that a second valve device is provided in parallel in a flow path, and when the flow rate decreases, the flow path is switched to a flow path only via the second valve apparatus. The above technical problems are drastically reduced by adopting a simple and rational configuration based on the above and switching the switching by the power of the fluid itself without using a complicated and expensive method such as an electric control device. It is easy to design, manufacture, and maintain, and the cost is low.It automatically and reliably controls the fluid pressure, etc., and it is difficult for chattering and hunting to occur.
It is an object to obtain a high-performance and economical automatic regulating valve device.

[0006]

SUMMARY OF THE INVENTION To achieve the above object, the present invention relates to an automatic regulating valve device which detects a change in the state of a fluid and controls the restriction of a flow passage. And a second automatic adjusting valve device are provided in parallel with each other, and an orifice is provided in the flow passage. When the flow rate of the flow decreases, the first automatic adjusting valve detects the decrease in the differential pressure across the orifice. The main feature is that a differential pressure pilot device for closing the device in preference to the second automatic regulating valve device is provided.

In the present invention, the diameter of the second automatic adjustment valve device may be smaller than the diameter of the first automatic adjustment valve device. Further, both the first automatic regulating valve device and the second automatic regulating valve device have a constant pressure control function for keeping the downstream pressure constant, a constant flow control function for keeping the downstream flow constant, and a constant downstream liquid level. A liquid level control function for maintaining the liquid level. Further, the first automatic adjustment valve device and the second automatic adjustment valve device may include a pilot valve device for opening and closing the valve body. Further, the second automatic adjustment valve device may be replaced with two automatic adjustment valve devices having a relationship between the first automatic adjustment valve device and the second automatic adjustment valve device.

With these configurations, in the automatic regulating valve device of the present invention, when the flow rate of the flow decreases, the first automatic regulating valve device first closes. At this time, the second automatic adjustment valve device remains in the valve open state, and the throttle control of the flow path is performed solely by the second automatic adjustment valve device alone, unless the flow rate increases again. When the second automatic adjustment valve device is closed, the flow path is completely closed. Conversely, when the flow rate increases again, the first automatic regulating valve device opens again,
The flow path is completely opened. That is, when the flow rate is high, both valve elements perform throttle control, and when the flow rate is low, throttle control is performed using only one of the valve elements. Since there is no need to narrow the flow path by approaching the valve seat to a close distance, chattering and hunting hardly occur. The effect becomes more remarkable when the diameter of the second automatic adjustment valve device is set smaller than the diameter of the first automatic adjustment valve device.

As described above, since chattering and hunting hardly occur, the durability of the valve body and the valve seat is improved, and stable liquid supply becomes possible. Also, when the flow rate is small, it is not necessary to narrow one of the flow passages by bringing one valve body close to the valve seat to a very short distance, so that the possibility of clogging is reduced even if the liquid supply contains foreign matter, It is also advantageous when used for applications other than cleaning liquids.

The switching between the operation of the first automatic adjustment valve device and the operation of the second automatic adjustment valve device is performed by the power of the fluid itself without using a complicated and expensive method such as an electric control device. Since the timing of switching the operation can be adjusted arbitrarily, it can easily respond to the situation at the facility site each time,
Extremely convenient in practice.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in more detail with reference to the drawings showing embodiments. In the drawings, common portions are denoted by common reference numerals. FIG.
1 shows a first embodiment in which the present invention is applied to a constant pressure valve. In FIG. 1, a first automatic regulating valve (constant pressure valve) device V and a second automatic regulating valve (constant pressure valve) device V ′ are connected to an inlet channel a1.
And the outlet flow path c, and are provided in parallel in the flow path.

The structures of the main valve device M and the pilot valve device P constituting the first automatic regulating valve device V are as follows.
Examples similar to those described with reference to the above-mentioned “Prior Art” and FIG. 7 are illustrated. That is, the main valve box 1 of the main valve device M
A main valve driving pressure chamber d for driving a main valve driving member 6 integrated with the main valve element 5 is formed therein. The main valve driving pressure chamber d is provided through an throttle adjustment valve 10 at an inlet flow path on the upstream side of the main valve. In addition, the pilot valve device P is closed when the downstream pressure of the main valve is higher than a predetermined value and is opened when the downstream pressure of the main valve is lower than a predetermined value, and is connected to the outlet flow passage c on the downstream side of the main valve. With this configuration, when the downstream pressure of the main valve becomes lower than the predetermined value, the pilot valve device P is opened, and the internal pressure of the main valve driving pressure chamber d becomes the downstream pressure of the main valve (hereinafter, also referred to as “secondary pressure”). ), The main valve 5 opens the valve by the thrust caused by the difference in the pressure receiving area between the main valve 5 and the main valve driving member 6 to increase the liquid supply. Is higher than a predetermined value, the pilot valve device P is closed, the internal pressure of the main valve driving pressure chamber d increases toward the main valve upstream pressure (hereinafter also referred to as “primary pressure”), and The valve element 5 closes to restrict the liquid supply and keeps the pressure downstream of the main valve constant. Although the main valve spring 9 in the figure is desirable for the stability of the operation of the main valve element 5 at the time of the first liquid passage, it is not a particularly essential member in the subsequent operation, and therefore may be omitted. Good.

Regarding the second automatic regulating valve device V ', the first
Although the diameter is smaller than that of the automatic adjusting valve device V, the main valve body 5 'of the main valve device M'; main valve driving member 6 '; main valve driving pressure chamber d'; Specifically, a device similar to the first automatic regulating valve device V is illustrated. Also, the structure of the attached pilot valve device P ′ is similar to that of the pilot valve device P. Therefore, detailed description of those internal structures is omitted. The internal pressures of the main valve drive pressure chambers d; d 'of the two valve devices V; V' are respectively controlled by pilot valve devices P; P ', and both serve as constant pressure valves for keeping the main valve downstream pressure at the same set secondary pressure. It is configured to work.

The apparatus further includes a structure for switching the operation of the two valve devices V; V '.
That is, an orifice 41 is provided in a flow passage passing through the main valve device M; M ', and is closed when a differential pressure across the orifice 41 is lower than a predetermined value, and is opened when the differential pressure is higher than a predetermined value. Q is serially provided in a communication passage t between the main valve driving pressure chamber d of the first automatic regulating valve device V and the pilot valve device P. The structure of the differential pressure pilot device Q is such that an orifice front pressure chamber j and an orifice rear pressure chamber k are provided with a pressure receiving plate 32 which is sealingly and slidably fitted on a cylindrical inner wall of a valve box 31 interposed therebetween. And pressure plate 3
An urging member 38 as a predetermined pressure means is connected to 2 and a valve body 33 which operates by the balance between the differential pressure between the two pressure chambers j and k and the opposing force between the predetermined pressure means opens and closes the communication passage t. I do. The orifice front pressure chamber j is communicated with a flow path a1 on the front face (upstream side) of the orifice 41, and the orifice rear pressure chamber k is provided on the rear face (downstream side) flow path a2 of the orifice 41.
Is communicated to.

An operation mode of the present invention will be described with reference to FIG. 1 showing a first embodiment applied to a constant pressure valve. FIG.
Is a state in which both the first automatic adjustment valve device V and the second automatic adjustment valve device V ′ are almost fully opened to supply liquid at a constant pressure, and operate as a constant pressure valve for maintaining downstream pressure. Is shown. Under this condition, if the flow rate of the main valve flow path is equal to or greater than a predetermined value, the difference between the internal pressures of the orifice front pressure chamber j and the orifice rear pressure chamber k of the differential pressure pilot device Q (ie,
Since the pressure difference between the front and rear of the orifice 41 exceeds the force of the urging member 38, the pressure receiving plate 32 is pushed upward in the drawing.
Therefore, the valve element 33 is in the open state and does not hinder the flow of the communication path t, and does not interfere with the operation of the first automatic regulating valve device V as a constant pressure valve.

Next, when the downstream pipe end is throttled, the two valve devices V; V 'start operating in the valve closing direction due to the original function of the constant pressure valve, but the downstream pipe end is further narrowed. Then, the resistance at the opening of the orifice 41 decreases, and
1, when the flow rate falls below a predetermined value, the force of the urging member 38 of the differential pressure pilot device Q is reduced to the pressure chambers j; k.
(That is, the differential pressure across the orifice 41), and the pressure receiving plate 32 is pushed downward in the figure. Therefore, the valve body 33 operates in the closing direction to restrict the communication passage t (that is, interferes with the operation as a constant pressure valve in priority), and the internal pressure of the main valve driving pressure chamber d increases toward the primary pressure, The main valve element 5 operates in the closing direction, and the first self-regulating valve device V closes preferentially.
At this time, the second automatic adjustment valve device V 'remains in the valve open state, and unless the flow rate increases again, the throttle control of the flow path, that is, the constant pressure control is performed exclusively by the second automatic adjustment valve device V'. Do. When the downstream end of the pipeline is closed, the second automatic regulating valve device V 'is also closed, and the flow path is completely closed.

Next, when the pipe terminal on the downstream side is opened again, the first automatic regulating valve device V 'is opened preferentially while the first automatic regulating valve device V remains closed, and the valve is exclusively opened. The throttle control of the flow path is performed only by the second automatic adjustment valve device V ′. When the downstream pipe terminal is further opened, the differential pressure across the orifice 41 increases and rises. When the flow rate exceeds a predetermined value, the difference between the internal pressures of the two pressure chambers j; k of the differential pressure pilot device Q ( That is, the differential pressure across the orifice 41) overcomes the force of the urging member 38, the valve body 33 returns to the open state, the first automatic regulating valve device V opens again, and the flow path is fully opened. Will be done. At this time, the differential pressure pilot device Q does not interfere with the operation of the first automatic adjustment valve device V as a constant pressure valve.

By operating the orifice 41 with the handle 42 or the like, the operation switching flow rate (ie, operation switching timing) of the two valve devices V; V 'can be set to a desired value. The urging member 38 to the urging force adjusting unit 38
By making the adjustment at a, the set value can be finely adjusted.

As described above, the first automatic regulating valve device V closes before the second automatic regulating valve device V 'when the flow rate decreases, and the second automatic regulating valve device closes when the flow rate increases. The valve opens later than V '. That is, when the flow rate is high, both valve elements perform throttle control, and when the flow rate is low, throttle control is performed using only one of the valve elements. Since there is no need to narrow the flow path by approaching the valve seat to a close distance, chattering and hunting hardly occur. The effect becomes more remarkable if the diameter of the second automatic adjustment valve device V ′ is set smaller than the diameter of the first automatic adjustment valve device V. As described above, since chattering and hunting hardly occur, the durability of the valve body and the valve seat is improved, and stable liquid supply becomes possible. Also, when the flow rate is small, it is not necessary to narrow one of the flow passages by bringing one valve body close to the valve seat to a very short distance, so that the possibility of clogging is reduced even if the liquid supply contains foreign matter, It is also advantageous when used for applications other than cleaning liquids.

The switching between the operation of the first automatic regulating valve device V and the operation of the second automatic regulating valve device V 'is performed by the power of the fluid itself without using a complicated and expensive method such as an electric control device. In addition, since the timing of the switching of the operation can be arbitrarily adjusted, it is possible to easily cope with the situation at the facility site each time, which is extremely practical in practice.

In this figure, for simplicity of explanation, the structures of both valve devices V; V 'are of the same type, but may be different constant pressure valves of the type having the same set secondary pressure. For example, it goes without saying that one may be a pilot-type constant-pressure valve and the other may be a direct-acting constant-pressure valve without a pilot.

FIG. 1 shows an example of a braking method when it is desired to operate the main valve device M; M 'of the two valve devices V; V' more slowly. (A damper) is shown. The structure of the main valve device M is, for example, that the cylindrical wall portion 3 of the main valve box 1 is provided with a reduced diameter portion, the main valve driving member 6 is provided with a large diameter portion, and the reduced diameter portion and the enlarged diameter portion are provided. A damper chamber 8 for damping the forward / backward movement of the main valve drive member 6 is formed between the damper chamber 8 and the diameter portion. By appropriately designing the shape of the damper chamber 8, or by providing a small hole communicating with the inside and the outside of the damper chamber 8 and adjusting the passing flow rate, the setting of the timing of the braking start and the adjustment of the braking force are performed. Needless to say, it can be done. It is shown that this mechanism can be applied to the main valve device M 'as well.

FIG. 2 shows a second embodiment in which the present invention is applied to a constant pressure valve. In this embodiment, the pilot valve device P 'attached to the second automatic adjustment valve device V' in the first embodiment is removed, and the pilot valve device P attached to the first automatic adjustment valve device V is used for the second automatic adjustment valve device. The valve device V ′ is also configured to be controlled together. That is, the pilot valve device P is a main valve driving pressure chamber d of both valve devices V; V '.
The internal pressure of d 'is controlled and both functions as a constant pressure valve. In this embodiment, a part of the communication passage t, that is, a portion between the pilot valve device P and the differential pressure pilot device Q is communicated with the main valve driving pressure chamber d 'of the second automatic regulating valve device V'. Accordingly, the opening and closing of the differential pressure pilot device Q affects only the first automatic adjustment valve device V. Other configurations and operation modes are the same as those of the first embodiment, and thus detailed description is omitted.

FIG. 3 shows a third embodiment in which the present invention is applied to a constant pressure valve. In this embodiment, the parts of the main valve device M; M 'of the two valve devices V; V' are the same as those of the first embodiment, but especially the pilot valve device P;
The basic part of P 'is described in International Publication WO 97/4566.
5 (International Application PCT / JP97 / 00042). The pilot valve device P attached to the first automatic regulating valve device V and the pilot valve device P 'attached to the second automatic regulating valve device V' are two valve devices V; V '.
, Respectively, and therefore, only the pilot valve device P will be described below, and description of the pilot valve device P ′ will be omitted.

The pilot valve device P is provided with a pilot A valve and a pilot valve B which operate in conjunction with each other by the balance between the downstream pressure of the main valve and the opposing force of the predetermined pressure means, so that the downstream pressure of the main valve becomes higher than a predetermined value. Open if open, close when low A
The valve and the main valve close when the downstream pressure becomes higher than a predetermined value,
The B-valve which opens when it is lowered is connected in series between the upstream side of the main valve and the downstream side of the main valve via the main valve driving pressure chamber d of the main valve device M in the middle thereof. I have.

In the valve box 21 of the pilot valve device P,
An A valve chamber f accommodating the A valve element 24, a B valve chamber h accommodating the B valve element 25, an intermediate chamber g between the A valve chamber f and the B valve chamber h, and a secondary pressure chamber i are formed. I have. A valve body 24 and B valve body 2
Numeral 5 is a cylinder / piston type valve opening / closing mechanism applied so as to be coaxial and cooperative with each other and not to hinder each other's operation. Further, at the time of operation, not only a state where one is opened and one is closed, but also both valve bodies 24 and 25 are arranged at a position interval which can produce a state of being substantially closed. Reference numeral 22 denotes a pressure receiving plate, 22 s denotes a seal member, and 26 denotes a valve shaft that combines the two valve bodies 24 and 25 integrally with the pressure receiving plate 22. The opposite side of the secondary pressure chamber i with respect to the pressure receiving plate 22 is open to the atmosphere, and an urging member 28 as a predetermined pressure means is mounted. This urging force, that is, the operating pressure of the pilot valve device P can be adjusted by the urging force adjusting unit 28a. The A valve chamber f is at the primary pressure of the inlet flow path a2, the intermediate chamber g is at the main valve driving pressure chamber d of the main valve device M, and the B valve chamber h is at the outlet flow path via a differential pressure pilot device Q described later. The secondary pressure chamber i is in communication with the secondary pressure of the outlet flow path c.

Now, assuming that the differential pressure pilot device Q is in an open state, and looking at the operation of the pilot valve device P itself, when the downstream pressure of the main valve becomes lower than a predetermined value,
The force of the biasing member 28 overcomes the internal pressure of the secondary pressure chamber i, the A valve element 24 closes, and the B valve element 25 opens, whereby the internal pressure of the main valve driving pressure chamber d decreases toward the secondary pressure. So
The main valve body 5 operates in the valve opening direction to increase the supply of liquid. Conversely, when the main valve downstream pressure becomes higher than a predetermined value,
The internal pressure of the secondary pressure chamber i overcomes the force of the biasing member 28, the A valve body 24 opens, and the B valve body 25 closes, whereby the internal pressure of the main valve driving pressure chamber d increases toward the primary pressure. So
The main valve body 5 operates in the closing direction to reduce the supply of liquid. As described above, the opening and closing of the valves A and B of the pilot valve device P are switched in response to the fluctuation of the downstream pressure of the main valve, the internal pressure of the main valve driving pressure chamber d is appropriately increased or decreased, and the downstream pressure of the main valve is reduced. Set 2
This serves as a constant pressure valve for maintaining the next pressure.

In this embodiment, the A valve body 24 and the B valve body 25 are provided on one valve shaft 26 so as to be aligned with each other and integrally with one predetermined pressure means (biasing member 28). do it,
The primary pressure and the secondary pressure are mixed in the pilot valve device P, and the combined pressure is sent to the main valve driving pressure chamber d to quickly respond to a change in the flow condition. Be quick. Further, when the secondary pressure is stable and stable, both the valve bodies 24 and 25 are stabilized in a substantially closed state, so that chattering and hunting during operation hardly occur. Further, since there is no fixed throttle portion in any of the flow path portions, it also has a feature that clogging of foreign matter in the liquid supply hardly occurs.

In addition to the function as the constant pressure valve, an operation switching function of the two valve devices V; V 'by the differential pressure pilot device Q is added. As in the case of the first embodiment, the orifice 41 is provided in the flow path flowing through the main valve device M; M ', and is closed when the pressure difference across the orifice 41 becomes lower than a predetermined value. A differential pressure pilot device Q, which opens when it becomes high, is serially interposed in the communication passage portion immediately after the B valve of the pilot valve device P, and exits from the main valve driving pressure chamber d via the communication passage t. The pilot flow path communicating with the flow path c is opened and closed.

The structure of the differential pressure pilot device Q is as follows.
As in the case of the embodiment, an orifice front pressure chamber j and an orifice rear pressure chamber k are provided with a pressure receiving plate 32, which is sealingly and slidably fitted on the cylindrical inner wall of the valve box 31, interposed therebetween. A biasing member 38 as a predetermined pressure means is connected to the pressure receiving plate 32, and the valve body 3 which operates by a balance between the differential pressure between the two pressure chambers j and k and the opposing force of the predetermined pressure means.
3 opens and closes the pilot flow path immediately after the B valve. The orifice front pressure chamber j is communicated with a flow path a1 on the front surface (upstream side) of the orifice 41, and the orifice rear pressure chamber k is communicated with a flow path a2 on the rear surface (downstream side) of the orifice 41.

Looking at the mode of operation, the A-valve element 24 and B
Under the state where the valve body 25 is working and operating as a constant pressure valve,
If the flow rate of the main valve flow path is equal to or greater than a predetermined value, the difference between the internal pressures of the orifice front pressure chamber j and the orifice rear pressure chamber k (ie, the differential pressure across the orifice 41) exceeds the force of the biasing member 38. Therefore, the pressure receiving plate 32 is pushed rightward in the figure. Accordingly, the valve element 33 is in the open state and does not obstruct the flow of the pilot flow path between the A valve and the B valve, so that it does not interfere with the operation of the first automatic adjustment valve device V as a constant pressure valve.

On the other hand, if the flow rate of the main valve flow path decreases to a predetermined value or less, the differential pressure across the orifice 41 decreases due to the decrease in the resistance of the opening of the orifice 41,
The force of the urging member 38 is equal to the difference between the internal pressures of the two pressure chambers j;
Pressure difference across the orifice 41), and the pressure receiving plate 32 is pushed leftward in the figure. Therefore, the valve element 33 operates in the closing direction to restrict the pilot flow path communicating with the outlet flow path c (that is, interferes with the operation as a constant pressure valve in preference), and the internal pressure of the main valve driving pressure chamber d becomes primary. The pressure rises toward the pressure, the main valve element 5 operates in the closing direction, and the first self-regulating valve device V closes preferentially. Conversely, when the flow rate increases, the differential pressure across the orifice 41 increases and increases accordingly, so that the difference between the internal pressures of the two pressure chambers j and k (ie, the differential pressure across the orifice 41) increases. , The valve element 33 returns to the open state, the first automatic adjustment valve device V opens again, and the differential pressure pilot device Q operates as a constant pressure valve of the first automatic adjustment valve device V. No longer interfere with

By operating the orifice 41 with the handle 42 or the like, the switching flow rate of the two valve devices V; V 'can be set to a desired value, and the urging member 38 can be adjusted by the urging force adjusting unit. By adjusting at 38a, the set value can be finely adjusted. This device has a dual valve device V with a differential pressure pilot device Q in addition to the function as a constant pressure valve;
Since the operation switching function of V 'is added, chattering and hunting hardly occur even when the flow rate is small, and stable operation is performed as in the first embodiment. Other configurations and operation modes are the same as those of the first embodiment, and thus detailed description is omitted.

FIG. 4 shows a fourth embodiment in which the present invention is applied to a constant pressure valve. In this embodiment, the pilot valve device P 'attached to the second automatic adjustment valve device V' in the third embodiment is removed, and the pilot valve device P attached to the first automatic adjustment valve device V is used for the second automatic adjustment device. The valve device V ′ is also configured to be controlled together. That is, the pilot valve device P is a main valve driving pressure chamber d of both valve devices V; V '.
The internal pressure of d 'is controlled and both functions as a constant pressure valve.

In this embodiment, the pilot valve device P
And the differential pressure pilot device Q are partitioned by a partition wall 35, and the intermediate chamber g of the pilot valve device P is communicated with the main valve driving pressure chamber d 'of the second automatic regulating valve device V', whereby the differential pressure pilot device Q is separated. The opening / closing of the device Q affects only the first automatic regulating valve device V. When the flow rate of the main valve flow path becomes equal to or less than a predetermined value and the valve element 33 of the differential pressure pilot device Q is closed, the primary pressure fluid on the inlet flow path a2 side is displaced by the main valve box cylindrical wall. 3 and main valve drive member 6
, The internal pressure of the main valve driving pressure chamber d increases toward the primary pressure, and the main valve element 5 is closed. For this reason, it is shown that the sealing member 6s of the main valve driving member 6 is intentionally reduced in sealing performance. It is needless to say that the inlet flow path a2 and the main valve driving pressure chamber d may be communicated with each other by a communication path with a throttle means instead of the method of reducing the sealing performance of the seal member 6s. Other configurations and operation modes are the same as those of the third embodiment, and thus detailed description is omitted.

FIG. 5 shows a fifth embodiment in which the present invention is applied to a constant pressure valve. In this embodiment, the orifice 4
1 is the flow path c on the downstream side of the main valve, contrary to the third embodiment.
1; c2, and the main valve driving member 6 of the first automatic regulating valve device V is provided on the downstream side of the main valve seat 4, contrary to the third embodiment. The arrangement of the A valve body and the B valve body of the device P; P 'is changed from that of the third embodiment to 1
They lived in two rooms. With these changes, the operating directions of the A valve body and the B valve body of the pilot valve device P; P 'are reversed, and each communication passage pipe is slightly different from that of the third embodiment. Although the arrangement position and the operation direction of the elements are different, other configurations and operations are the same as those of the third embodiment.

The orifice 41 of this embodiment is also exemplified as a fixed orifice. In this case, the setting of the operation switching flow rate of the two valve devices V; V 'can be performed by adjusting the urging member 38 by the urging force adjusting unit 38a. In particular, when it is desired to minimize the occurrence of a detection error of the differential pressure due to turbulence when an on-off valve type orifice is mounted, the use of a fixed orifice is an effective means. Even in the case of a fixed orifice, it is desirable that the orifice be recombinable. Further, a groove may be formed around the pressure detection port before and after the orifice to prevent the pressure difference before and after the orifice from being affected by the turbulent flow. However, since this method is well known in the related art, a detailed description will be omitted. . By opening and closing means at an appropriate position in the pilot flow path of the pilot valve device P; P 'and closing the same, the two valve devices V; V' are forcibly closed at the time of maintenance or the like. In the case of the present embodiment, the on-off valve 11; 11 'may be provided.
Other configurations and operation modes are the same as those of the third embodiment, and thus detailed description is omitted.

FIG. 6 shows a sixth embodiment in which the present invention is applied to a constant pressure valve. In this embodiment, the pilot valve device P 'attached to the second automatic adjustment valve device V' in the fifth embodiment is removed, and the pilot valve device P attached to the first automatic adjustment valve device V is used for the second automatic adjustment valve device. The valve device V ′ is also configured to be controlled together. That is, the pilot valve device P is a main valve driving pressure chamber d of both valve devices V; V '.
The internal pressure of d 'is controlled and both functions as a constant pressure valve. And the main valve drive member 6 'of the second automatic regulating valve device V' is also
It is also exemplified that the type of the main valve device M; M 'can be freely selected and combined, for example, it may be provided on the downstream side of the main valve seat similarly to the main valve drive member 6 of the first automatic regulating valve device V. I have.

In this embodiment, the pilot valve device P
Is communicated with the main valve driving pressure chamber d 'of the second automatic regulating valve device V', whereby the differential pressure pilot device Q
Opening / closing affects only the first automatic regulating valve device V. When the flow rate of the main valve flow path becomes equal to or less than a predetermined value and the valve element 33 of the differential pressure pilot device Q is closed, the pressure fluid in the main valve driving pressure chamber d is released by the main valve box cylindrical wall. The internal pressure of the main valve driving pressure chamber d decreases toward the secondary pressure by leaking to the outlet flow path c1 through the gap between the main valve driving member 6 and the main valve driving member 6, and the main valve body 5 It is closed. For this reason, it is shown that the sealing member 6s of the main valve driving member 6 is intentionally reduced in sealing performance. Instead of reducing the sealing performance of the seal member 6s, the main valve driving pressure chamber d and the outlet flow path c1
Needless to say, these may be communicated with each other through a communication passage provided with a throttle means. In addition, it is also possible to forcibly close both valve devices V; V ′ at the time of maintenance or the like by providing an opening / closing means at an appropriate position in the pilot flow path of the pilot valve device P and closing the opening / closing means. It is also possible that the on-off valve 11 may be provided in this embodiment. Other configurations and operation modes are the same as those of the fifth embodiment, and thus detailed description is omitted.

As described above, the automatic regulating valve device of the present invention produces an epoch-making operation and effect. However, within the scope of the present invention, various structural changes are made or the prior art is used. It is possible to meet implementation requirements. For example, as for the main valve device M, the lift valve type is applied to the main valve element 5 in each embodiment, but other types of on-off valves (for example, butterfly valve, A gate valve, a ball valve, etc.) may be applied. In addition,
FIGS. 1 to 4 illustrate an example in which the main valve body 5 and the main valve drive member 6 are formed as an integral member, and FIGS. 5 to 6 illustrate an example in which this is divided into respective members. The main valve body 5 and the main valve driving member 6 are housed in each of two divided main valve boxes, and the main valve body 5 and the main valve driving member are provided at both ends of a main valve shaft penetrating the two valve boxes. 6 may be fixed. These points can be similarly applied to the main valve device M ′.

The pilot valve device P illustrated in FIGS.
With respect to the structure of (1), the A valve body 24 and the B valve body 25 may be disposed in the A valve chamber f and the B valve chamber h, respectively, or may coexist in the intermediate chamber g. Further, the valve bodies 24 and 25 may be provided on separate valve shafts. These points can be similarly applied to the pilot valve device P ′. In addition, various designs such as the arrangement (positional relationship) and combination of the respective chambers f; g; h; i; j; k of the pilot valve device and the differential pressure pilot device, and the accompanying communication passage piping, can be changed. Is not limited to the above embodiments. Regarding the urging member as the predetermined pressure means, a coil spring is illustrated in each drawing, but other elastic members may be used, a weight may be linked, a booster may be added, and a pressure and hydraulic device may be used. Needless to say, it may be applied.

In FIGS. 1, 3 and 5, both valve devices V;
Although the same type of pilot valve device P; P 'is provided for each of the V's, a different type of pilot valve device may be provided for each of the two valve devices V; V'. Further, one may be a pilot drive system, the other may be a direct drive system without using a pilot, or both may be a direct drive system. However, in either case, it is desirable to match the characteristics of the two valve devices V; V '(for example, in the case of a constant pressure valve, the set secondary pressure). In addition, a safety valve may be installed in an appropriate place for safety management of the equipment.

Depending on the specification conditions, in order to more reliably prevent chattering and hunting, as shown in each figure, the main valve opening b of the main valve device M; A road shape, a damper 8 may be formed, or another braking means may be provided.
Also, the pilot valve device P; P '
There is also a method such as appropriately narrowing the communication passage. Any of these countermeasures may be employed alone, or some of them may be employed in combination, or may be omitted under specification conditions in which it is not required.

As for the orifice 41 interposed for switching the operation of the two valve devices V; V ', when it is made variable, a general on-off valve (for example, butterfly valve, gate valve, ball valve) , Lift valve, etc.). Since the orifice 41 does not need to have a sealing performance, a seal for the valve seat can be omitted. Regarding the operation, of course, besides the manual operation using the handle 42, it is also possible to automate the operation for setting the operation switching flow rate of the two valve devices V; V ′ using various actuators and the like. The orifice 41 can be installed either upstream or downstream of the main valve.
Also, the predetermined pressure means (the urging member 3) of the differential pressure pilot device Q
In the case where the biasing force adjusting section 38a is provided in 8), since the adjustment of the predetermined pressure means means the setting of the flow rate, the flow rate setting by the throttle operation of the orifice 41 is not necessarily required, and the orifice 41 is fixed. Orifices may be used. Of course, it is desirable to allow recombination even with a fixed orifice.

Opening / closing means 10; 1 provided in the communication passage
Regarding 0 ';11;11', etc., any type having an opening / closing function may be used, for example, a needle valve, a ball valve,
Needless to say, a ball valve, a cock and the like can be appropriately selected. Over each embodiment, as for the seal member to be attached to the place where the sealing property is required, an O-ring, a packing, a seal ring, a diaphragm, a bellows, etc. may be applied as appropriate in accordance with the local specifications, or by direct contact. If good sealing performance can be maintained, the sealing member may be omitted. In addition, conventional techniques such as making the shape of the contact surface between each valve element and the valve seat into a cone shape or a curved surface, or providing a comb-shaped projection or a rectifying grid on the valve element or the valve seat to prevent cavitation are used. May be.

In the above, the number of the automatic control valve devices has been described as two. However, the number of the automatic control valve devices may be three or more to configure a valve device adapted to a larger pipe. is there. For example, the second automatic regulating valve device V '
There is a method of replacing three automatic adjusting valve devices with two automatic adjusting valve devices having a relationship between the automatic adjusting valve device V and the second automatic adjusting valve device V ′ so that three automatic adjusting valve devices are arranged in parallel. . Since this point is obvious from the above description, illustration is omitted.

The technical idea of the present invention can be applied not only to the automatic regulating valve for performing the constant pressure control illustrated in each embodiment but also to the automatic regulating valve for performing the constant flow rate control, the liquid level control and the like. Needless to say. In addition, various design changes can be made within the scope of the present invention, and the present invention is not limited to the above embodiments.

[0048]

As described above, in the automatic regulating valve device of the present invention, when the flow rate is large, both the valve bodies perform the throttle control, and when the flow rate is small, the throttle control is performed by only one of the valve bodies. Since there is no need to narrow the flow path by bringing one valve element close to the valve seat at a small flow rate when the flow rate is small as in the prior art, chattering and hunting hardly occur. Therefore, the durability of the valve body and the valve seat is improved, and a stable liquid supply becomes possible. Also, clogging of foreign matter is unlikely to occur. The switching of the operation of the automatic regulating valve device is performed by the power of the fluid itself without using a complicated and expensive method such as an electric control device, and the timing of the switching of the operation can be arbitrarily adjusted. It can easily respond to the situation at the facility site each time, and is extremely convenient in practice.

As described above, the present invention has a simple and rational structure based on a simple and clear principle, and is easy to design, manufacture, and maintain, and is inexpensive, and automatically and reliably controls fluid pressure and the like. In addition, a high-performance and economical automatic adjusting valve device is obtained in which chattering and hunting hardly occur and foreign matter is hardly clogged. Therefore, the remarkable effect of the implementation is extremely large as compared with the prior art.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a first embodiment of an automatic regulating valve device of the present invention, showing an application example to a constant pressure valve.

FIG. 2 is a longitudinal sectional view of a second embodiment of the automatic regulating valve device of the present invention, showing an example of application to a constant pressure valve.

FIG. 3 is a longitudinal sectional view of a third embodiment of the automatic regulating valve device according to the present invention, showing an example of application to a constant pressure valve.

FIG. 4 is a longitudinal sectional view of a fourth embodiment of the automatic regulating valve device according to the present invention, showing an application example to a constant pressure valve.

FIG. 5 is a longitudinal sectional view of a fifth embodiment of the automatic regulating valve device according to the present invention, showing an application example to a constant pressure valve.

FIG. 6 is a longitudinal sectional view of a sixth embodiment of the automatic regulating valve device of the present invention, showing an example of application to a constant pressure valve.

FIG. 7 is a longitudinal sectional view showing an example (constant pressure valve) of a conventional automatic regulating valve device.

[Explanation of symbols]

V: first automatic regulating valve device M: main valve device 1: main valve box 2: main valve box cover 3: cylindrical wall portion 4: main valve seat 5: main valve body 6:
Main valve drive member 6s Seal member 7 Main valve shaft 8 Damper (chamber) 9 Main valve spring 10 Throttle adjusting valve 11 Open / close valve a (a1; a2) Main valve inlet flow path b Main valve opening Part c (c1; c2): Main valve outlet flow path d: Main valve driving pressure chamber V ': Second automatic regulating valve device M': Main valve device 5 '
... Main valve element 6 '... Main valve drive member 10' ... Throttle adjusting valve 11 '
... On-off valve d '... Main valve drive pressure chamber P ... Pilot valve device (for first automatic adjustment valve device) 21
... Valve box 22 ... Pressure receiving plate 22s ... Seal member 23 ... Valve body 24 ... A valve body
25 ... B valve element 26 ... Valve shaft 28 ... Biasing member 28a ... Biasing force adjusting part P '... Pilot valve device (for the second automatic regulating valve device) Q ... Differential pressure pilot device 31 ... Valve box 32 ... Pressure receiving plate 33 ... valve element 35 ... partition wall 38 ... urging member 38a ... urging force adjusting part f ... A valve chamber g ... intermediate chamber h ... B valve chamber i ... secondary pressure chamber j ... orifice front pressure chamber k ... orifice rear pressure chamber t ... communication passage 41 ... orifice 42 ... handle

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Kunio Ogura, Inventor 1-3-6 Minamiyoshijima, Naka-ku, Hiroshima City, Hiroshima Prefecture Inside Yokota Manufacturing Co., Ltd. (72) Masayuki Akiyama 1-chome, Minamiyoshijima, Naka-ku, Hiroshima City, Hiroshima Prefecture No.3-6 F-term in Yokota Manufacturing Co., Ltd. (Reference) 3H056 AA01 BB12 BB32 BB37 BB41 BB49 CA01 CB03 CB05 CC05 CC07 CD01 CE03 DD02 DD10 EE01 EE06 GG04 3H060 AA02 BB03 BB10 CC35 CC36 DD05 DD13 DD17 DF08 GG00

Claims (5)

[Claims] 1. An automatic regulating valve device which senses a change in the state of a fluid and controls the throttle of a flow path, wherein a first automatic regulating valve device and a second automatic regulating valve device are provided in parallel in the flow passage, An orifice is provided in the flow passage, and when the flow rate is reduced, the decrease in the differential pressure across the orifice is sensed to close the first automatic adjustment valve device in preference to the second automatic adjustment valve device. An automatic regulating valve device comprising a pressure pilot device. 2. The automatic regulating valve device according to claim 1, wherein a diameter of the second automatic regulating valve device is smaller than a diameter of the first automatic regulating valve device. 3. A constant pressure control function for keeping the downstream pressure constant, wherein the first automatic adjustment valve device and the second automatic adjustment valve device are both provided.
The automatic regulating valve device according to claim 1, further comprising: a constant flow rate control function for keeping the downstream flow rate constant, or a liquid level control function for keeping the downstream fluid level constant. 4. . 4. The automatic valve control device according to claim 1, wherein the first and second automatic adjustment valve devices include a pilot valve device for opening and closing the valve body. 3. The automatic regulating valve device according to claim 1. 5. The automatic valve control apparatus according to claim 2, wherein the second automatic regulating valve device has a relationship between the first automatic regulating valve device and the second automatic regulating valve device.
An automatic regulating valve device characterized by being replaced by a plurality of automatic regulating valve devices.