JPH0339644Y2 - - Google Patents

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a constant flow valve used in pipes for transporting fluids such as tap water, industrial water, agricultural water, petroleum, or chemical liquids that require a constant supply. It is something.

[Conventional technology]

Conventionally, known automatic regulating valves for constant flow control include constant flow valves that have a constant flow control function and a function to change the set flow rate, and constant flow valves that have a constant flow control function and an opening/closing function. ing. The former is described in Japanese Patent Publication No. 57-57729 as "Fixed flow rate automatic control valve"
The latter is disclosed as a "fluid valve" in Japanese Unexamined Patent Publication No. 59-231274.

[Problem that the invention attempts to solve]

The "Fixed flow rate automatic control valve" disclosed in the above-mentioned Japanese Patent Publication No. 57-57729 is a bellofram type automatic control valve that has a flow constriction section in the flow path inside the valve box and moves by sensing the pressure difference that occurs before and after the flow constriction section. A differential pressure regulating valve keeps the pressure difference constant and performs constant flow control, and an umbrella-shaped adjustment device for contracting flow adjusts the width and narrowness of the contracting flow section, making it possible to change the set flow rate. . However, this model and other well-known models equipped with a diaphragm type differential pressure regulating valve and a throttle valve do not have an opening/closing mechanism due to their structure when the need for emergency closing arises. , a stop valve shall be provided.

In addition, the "fluid valve" disclosed in Japanese Patent Application Laid-open No. 59-231274 incorporates a flow rate adjustment valve inside a ball valve to enable constant flow rate control and opening/closing operations, but the set flow rate cannot be changed. It does not have a change function.

As described above, in the prior art, there is still no constant flow valve that has the three functions of constant flow control, changing the set flow rate, and opening/closing at the same time and has a simple structure and is compact.

In view of the above-mentioned circumstances, the present invention automatically maintains the set flow rate even if the fluid pressure on the upstream and downstream sides of the valve fluctuates greatly, allows the set flow rate to be easily changed, and allows for changes from low differential pressure to high differential pressure. The present invention aims to provide a simple and compact constant flow valve that can control the flow rate over a wide range of pressures and can also stop the flow of fluid if necessary.

[Means for solving problems]

The structure of the present invention for solving the above problems will be explained with reference to FIGS. 1, 2, and 3, which correspond to embodiments thereof.

The constant flow valve of the present invention has a partition wall 1 provided inside.
The inlet flow path 2 has a curved flow path, the outlet flow path 3 has an axis line arranged at a certain angle with respect to the axis of the inlet flow path 2, and the inlet flow path 2 and the outlet flow path 3 have a curved flow path. a stop valve type valve body 5 having a hollow chamber 4 located between the stop valve body 5, provided within the valve body 5;
An opening 7 that connects the inlet channel 2 and the hollow chamber 4 and has an inner circumferential surface that is tapered in diameter from the downstream side toward the upstream side, a lid body 9 attached to the valve body 5, and the lid. a spindle 1 supported by a body 9, having an axis that coincides with the axis of the opening 7 and capable of moving forward and backward in the axial direction;
1. A sealing surface 1 that is integrally provided at the lower end of the spindle 11, is mounted so as to be movable forward and backward within the hollow chamber 4 so as to communicate with the opening 7, and is provided at the lower end thereof.
4a is a cylinder 14 that can come into contact with the valve seat 6 of the opening 7; a through hole 16a that is slidably fitted into the cylinder 14 and communicates with the opening 7;
and is located on the same axis as the opening 7 and always forms an orifice 8 between the valve body 1 and the opening 7.
6. Disposed between the valve body 16 and the cylinder 14 so that the valve body 16 is biased away from the opening 7 and the timings at which expansion and contraction in response to fluctuations in fluid pressure begin are substantially different from each other. It comprises a first spring 17a and a second spring 17b having different spring constants.

The material of the constant flow valve of the present invention may be plastic or metal, and is not particularly limited.

[Effect]

Figure 1 shows the operation of the constant flow valve of the present invention with the above configuration.
This will be explained with reference to FIGS. 2 and 3.

In FIG. 1, when the fluid flows, the opening 7
A part of the fluid that has reached the through hole 16a of the valve body 16
The other part passes through the orifice 8 formed between the opening 7 and the valve body 16 and reaches the hollow chamber 4 of the valve body 5.
A part of the fluid passing through the hollow chamber 4 flows into the secondary pressure chamber 15b between the cylinder 14 and the valve body 16.

As shown in Fig. 2, the fluid pressure upstream of the orifice 8 is P ₁ , and the fluid pressure downstream is P ₂
Then, the primary pressure chamber 15a becomes P ₁ and the secondary pressure chamber 15b becomes P ₂ . Therefore, when a pressure difference occurs between the fluid on the upstream side and the downstream side of the orifice 8, a pressure difference equal to this pressure difference occurs in the primary pressure chamber 15a.
and the secondary pressure chamber 15b, and this pressure difference causes the valve body 16 to release the first spring 17a (first and second springs 17a,
17b), or upward while being urged by the first spring 17a (first and second springs 17a, 17b in FIG. 3). The orifice 8 is expanded or contracted by the vertical movement of the valve body 16, and the flow rate of the fluid passing through the orifice 8 is automatically adjusted to the set value accordingly.

On the other hand, the opening 7 has a pre-designed shape that allows for a wide range of flow rate settings, but if a pressure difference that exceeds the design differential pressure range occurs at any set value, the valve The dynamic equilibrium state between the force that moves the body 16 and the elastic repulsive force of the first spring 17a (first and second springs 17a, 17b in FIG. 3) is continuously disrupted,
The valve body 16 tries to rapidly move toward the upstream side.

However, at this time, first, the first spring 17a
After the valve body 16 moves over a certain distance by compressing the spring 17b, the valve body 16 receives a strong elastic repulsive force mainly from the second spring 17b. Therefore, rapid movement of the valve body 16 is prevented, and a stable dynamic equilibrium state can be maintained again. In order to make this effect effective, the second
It is desirable to use a spring 17b with as large a spring constant as possible.

Furthermore, when the spindle 11 and cylinder 14 are moved up and down, the valve body 16 is also moved up and down accordingly, changing the opening area of the orifice 8. Thereby, the set value of the flow rate can be arbitrarily adjusted to a large or small value.

Furthermore, the spindle 11 and the cylinder 14
When the lower end sealing surface 14a of the cylinder 14 finally comes into contact with the valve seat surface 6 of the opening 7, the space between the inlet flow path 2, the hollow chamber 4 and the outlet flow path 3 is completely closed. It is occluded, stopping fluid flow and the valve is completely closed.

〔Example〕

An embodiment of the present invention will be described with reference to FIGS. 1 to 6.

1 and 2 show a first embodiment of the present invention, which is a Y-shaped structure in which the axis of the hollow chamber 4 is arranged obliquely with respect to the axis of the inlet flow path 2. It is a constant flow valve.

In FIG. 1, reference numeral 5 denotes a stop valve type valve body, which has an inlet flow path 2 and an outlet flow path 3 in which the flow paths are curved by a partition wall 1 provided inside, and a flow path between the inlet flow path 2 and the outlet flow path. Hollow chamber 4 located between the passageway 3
have.

7 is an opening provided in the valve body 5,
It is formed by the partition wall 1 and the inner wall of the valve body 5 located at the bottom of the hollow chamber 4, communicates the inlet channel 2 with the hollow chamber 4, and has a valve seat section 6 at its tip. The opening 7 is provided with a flow path changed in a diagonal direction with respect to the axis of the inlet flow path 2, and its inner circumferential surface is reduced in diameter from the downstream side to the upstream side. In this embodiment, the shape of the inner circumferential surface of the opening 7 is directly shaped into the opening 7, but by attaching a cylindrical body having an inner circumferential surface shaped into the above-mentioned shape. An opening 7 may also be formed.

Reference numeral 9 denotes a lid body, which has an opening 9a in the center of its upper end.
Its lower end is fitted into the hollow chamber 4 of the valve body 5, the flange 9b protruding from the outer circumferential surface is brought into contact with the upper end of the valve body 5, and the outer circumference of the valve body 5 is screwed. It is fixed to the valve body 5 by tightening the flange 9b with the fitted cap nut 10.

The opening 9a of the lid 9 holds a spindle 11 whose axis is aligned with the axis of the opening 7, and a bush 12 screwed onto the spindle 11.

Reference numeral 14 denotes a cylinder, which is integrally molded at the lower end of the spindle 11 and has a hollow chamber 1 inside.
5. This cylinder 14 has an opening 7
The lower part and the lower end sealing surface 14a are installed in the hollow chamber 4 of the valve body 5, and the other upper part is installed in the lid body 9 so as to be slidable and movable back and forth. ing. A pair of guides 14b are provided on the outer circumference of the cylinder 14 so as to face each other in the diametrical direction, and are engaged with a pair of guide grooves 9c provided on the lower inner circumferential surface of the lid body 9.
Only vertical movement is possible. Note that a gasket may be attached to the lower end sealing surface 14a of the cylinder 14 in order to improve the sealing performance when the valve is closed.

16 is a piston-shaped valve body, which has an axial through hole 16a inside and a flange 16b at its upper end.
Further, each of the flange portions 16b has an annular protrusion portion 16c on the lower peripheral edge thereof, and is slidably mounted in the hollow chamber 15 of the cylinder 14. This valve body 16 is located on the same axis as the opening 7, and its length is set so that an orifice 8 can always be formed between the valve body 16 and the opening 7. Note that the valve body 16 is not limited to one formed by integral molding as shown in FIG.
It may be formed by attaching a separately provided valve body piece 16d having a flat plate-like flange, a valve body piece 16e having a truncated conical flange, etc. as shown in FIGS. A and B.

17a and 17b are first and second springs, and the upper end of the first spring 17a abuts against the flange 16b of the valve body 16, and the lower end abuts against a first spring seat 18 described later. It is installed like this. The upper end of the second spring 17b is mounted so as to come into contact with a second spring seat 19, which will be described later, and the lower end thereof is mounted so as to come into contact with a first spring seat 18.

18 is the first spring seat, and the cylinder 14
To allow fluid to flow into and out of the
It is fixed to the lower end of the inner periphery of this cylinder 14. The shape of the spring seat 18 is not particularly limited, but a ring shape is preferred in order to prevent the valve body 16 from swinging, and a preferred embodiment thereof is shown in FIG. The one shown in FIG. 5A is provided with a flow groove 18a on the inner peripheral surface in contact with the valve body 16, and the one shown in FIG. 5B is provided with a plurality of through holes 18b. It is something that

19 is a second spring seat, and the cylinder 14
The first spring 1 is slidably fitted into the inner circumferential surface of the spring 1, and has a through hole in the center of the first spring 1.
It is inserted through and arranged so that 7a does not touch.
After the valve body 16 moves downward for a certain distance, its projection 16c comes into contact with the second spring seat 19, and from then on the second spring seat 19 can move together with the valve body 16. ing.

A handle 13 is fixed to the bush 12 and engages with the spindle 11 via the bush 12. In FIG. 1, the handle 13
When the spindle 11 and cylinder 14 are rotated, the structure is such that the spindle 11, cylinder 14, etc. can only move up and down. However, this is not limited to this; the handle 13 is directly fixed to the spindle 11, and the rotation of the handle 13 According to the movement, the spindle 11, cylinder 14, etc. may also be structured to rotate and move forward and backward, and the operation will not change.

The operation of this embodiment having the above configuration is as follows.

First, when fluid is allowed to flow in the state shown in FIG. The other part is introduced into the primary pressure chamber 15a in the hollow chamber 15 of the cylinder 14, and the other part passes through the orifice 8 formed by the opening 7 and the valve body 16, and passes through the hollow chamber 4 of the valve body 5 to the outlet. It flows out into the flow path 3. During this process, a part of the fluid passing through the hollow chamber 4 flows through the flow groove 1 provided in the first spring seat 18.
It is introduced into the secondary pressure chamber 15b in the hollow chamber 15 of the cylinder 14 through 8a. Note that the primary pressure chamber 15a and the secondary pressure chamber 15b in the hollow chamber 15 of the cylinder 14 are independent chambers, and the valve body 1
6 is slidably fitted into the cylinder 14 by its flange 16b, so that fluid does not leak.

Now, as shown in FIG. 2, if the fluid pressure on the upstream side of the orifice 8 is P ₁ and the fluid pressure on the downstream side is P ₂ , then in the primary pressure chamber 15a,
Since the fluid upstream from the orifice 8 is introduced, a pressure of _P1 is applied to the primary pressure chamber 15a. That is, a pressure of P ₁ is applied to the upper surface of the flange portion 16b of the valve body 16. On the other hand, since the fluid on the downstream side of the orifice 8 is introduced into the secondary pressure chamber 15b, a pressure of _P2 is applied thereto.
Therefore, when a pressure difference occurs between the fluids on the upstream side and the downstream side of the orifice 8, a pressure difference equal to this pressure difference occurs between the primary pressure chamber 15a and the secondary pressure chamber 15b, and the valve body 16 The force generated by the pressure difference between the upper and lower surfaces of the portion 16b urges the first spring 17a downward, or conversely, the first spring 17a.
It moves upward while being urged by the spring 17a.

By this vertical movement of the valve body 16, the orifice 8 is expanded or contracted, and the flow rate of the fluid passing through the orifice 8 is automatically adjusted accordingly.

That is, for example, in the state shown in FIG. 1, if the fluid pressure on the upstream side of the orifice 8 increases or the fluid pressure on the downstream side of the orifice 8 decreases, the flow velocity of the fluid passing through the orifice 8 increases, The flow rate increases above the set value. However, since the pressure difference P ₁ - _{P 2} generated between the upstream and downstream sides of the orifice 8 becomes large, the valve body 16 having the flange 16b
moves downward in response to the pressure difference, and the opening area of the orifice 8 is further reduced, so the flow rate is reduced and adjusted to the set value.

On the other hand, if the flow rate decreases below the set value due to pressure fluctuations, the opening area of the orifice 8 will increase using the same principle as above and the opening area of the orifice 8 will increase, and the flow rate will automatically increase and be adjusted to the set value. .

On the other hand, the opening 7 has a pre-designed shape that allows for a wide range of flow rate settings;
If a pressure difference that exceeds the design differential pressure range occurs at any set value, the dynamic equilibrium state between the force that moves the valve body 16 and the elastic repulsive force of the first spring 17a is continuously disrupted. , the valve body 16 tries to rapidly move toward the upstream side. At this time the second
The spring 17b functions to prevent rapid movement of the valve body 16. That is, when the valve body 16 moves downward in a certain section, the protrusion 16c
comes into contact with the second spring seat 19, and thereafter the valve body 16 and the spring seat 19 move together, so that the valve body 16
is mainly subjected to a strong elastic repulsive force from the second spring 17b. Therefore, rapid movement of the valve body 16 is prevented, and a stable dynamic equilibrium state can be maintained again. In order to make this effect effective, it is desirable that the second spring 17b has a spring constant as large as possible.

Next, when the handle 13 is rotated in the opening direction from the state shown in FIG. 1 and the spindle 11 and cylinder 14 are moved upward, the valve body 16 is also moved upward accordingly, so the opening area of the orifice is becomes larger and the flow rate increases. In this way, the set value can be increased. In this state, even if the fluid pressure on the upstream side of the orifice 8 increases or the fluid pressure on the downstream side decreases, the flow rate is automatically adjusted by the actions of each part as described above, and this new set value remains constant. will be maintained.

On the other hand, when the handle 13 is rotated in the closing direction from the state shown in FIG.
As the flow rate also moves downward, the opening area of the orifice 8 becomes smaller and the flow rate decreases. In this way, the set value can be reduced. This new set value is also maintained constant by the same action as described above.

Continuing from the above, when the handle 13 is further rotated in the closing direction, the spindle 11 and the cylinder 14 move further downward, and the lower end sealing surface 14a of the cylinder 14 finally touches the valve seat part 6 of the valve body opening 7. Since the pressure contact is made, the flow of fluid from the opening 7 to the hollow chamber 4 of the valve body 5 and the outlet channel 3 can be completely stopped. That is, this constant flow valve is completely closed.

FIG. 3 shows a second embodiment of the invention.

In this embodiment, a first spring 17a and a second spring 17b are arranged in series with a second spring seat 19 in between. The other configurations are the same as those in the first embodiment, so the explanation will be omitted.

The first spring 17a is disposed such that its upper end abuts against the flange 16b of the valve body 16, and its lower end abuts against the upper end of the second spring seat 19.
The spring 17b is disposed such that its upper end abuts on the lower surface of the second spring seat 19, and its lower end abuts on the first spring seat 18. The second spring seat 19 is a perforated spring seat, and is disposed so as to be fitted onto the outside of the shaft portion of the valve body 16 so as not to come into contact with the valve body 16, and is slidable on the inner circumferential surface of the cylinder 14. It is fitted.

Regarding the operation of this embodiment having the above configuration, the valve body 16, the first and second springs 17
Only the relationship between a, 17b and the second spring seat 19 will be explained, and the other details will be omitted because they are the same as in the first embodiment.

In FIG. 3, when a pressure difference is applied between the upper and lower surfaces of the flange 16b of the valve body 16, the valve body 16 receives the force and biases the first spring 17a and the second spring 17b. Conversely, it moves up and down while being biased by these springs. If a pressure difference that exceeds the design pressure difference occurs, the force that moves the valve body 16 and the first and second springs 17
The dynamic balance with the elastic repulsive forces from a and 17b cannot be maintained, and the valve body 16 tries to move downward rapidly, but when it moves downward for a certain period, the protrusion 16c of the valve body 16 is moved by the second spring. The spring seat 19 comes into contact with the seat 19, and thereafter the spring seat 19 moves together with the valve body 16. That is, since the valve body 16 mainly receives a strong elastic repulsive force from the second spring 17b, rapid downward movement is prevented, and a stable dynamic equilibrium state can be maintained again. In order to make this effect effective, it is desirable that the second spring 17b has a spring constant as large as possible.

Figure 6 shows a diameter 50A with the structure shown in Figure 1.
constant flow valve (however, the spring constant of the first spring 17a is 0.4, the spring constant of the second spring 17b is
1.0) under the following conditions.

[Conditions] Fluid: Water at room temperature Flow rate setting range at the opening: 2.0 to 8.0 m ³ /hr Pressure difference before and after the valve: 0 to 1.5 Kgf/cm ² As can be seen from the graph, the constant flow valve of this example has a flow rate of 2.0 m ³ The flow rate can be set arbitrarily in the range of /hr to 8.0m ³ /hr, and each set value can be maintained within ±3% to ±6%, and it can also be adjusted from low pressure (0.15Kg/cm ² ) to high pressure (1.5Kgf). /cm ² ), it operated stably over a wide range of pressure differences.

[Effect of idea]

Since the present invention has the above-described configuration and operation, it has the following effects.

Even if the fluid pressure difference between the upstream and downstream sides fluctuates significantly, the preset flow rate can be automatically maintained constant.

With a simple operation, the flow rate setting value can be changed over a wide range from low differential pressure to high differential pressure, and the changed setting value can be maintained constant.

Since it has a valve opening/closing function, there is no need to provide a separate stop valve.

Constant flow rate control is possible with very small pressure loss.

Because the structure is simple and compact, it can be manufactured at low cost and does not take up much space when piping.
Also, maintenance and inspection can be easily performed.

As described above, according to the present invention, constant flow control,
A constant flow valve is obtained that has three functions simultaneously: changing the flow rate setting value and opening/closing.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of the first embodiment of the present invention, and the second
The figure is a vertical cross-sectional view of the main part of the same embodiment as above, FIG. 3 is a vertical cross-sectional view of the main part of the second embodiment of the present invention, and FIG. Fig. 2 is a vertical cross-sectional view showing an example in which the valve body piece A has a plate-like flange, and B shows a valve body piece whose flange has a truncated cone shape. FIG. 5 is a plan view showing a first spring seat according to an embodiment of the present invention, in which A shows a spring seat with a groove provided on the inner circumferential surface, and B shows a spring seat with a through hole provided in the main body. FIG. 6 is a graph showing the results of an actual flow test using the embodiment of the present invention. DESCRIPTION OF SYMBOLS 1... Partition wall, 2... Inlet channel, 3... Outlet channel, 4... Hollow chamber, 5... Valve body, 6... Valve seat, 7... Opening, 8... Orifice, 9 ... Lid body, 11 ... Spindle, 13 ... Handle, 1
4...Cylinder, 14a...Lower end sealing surface, 1
5... Cylinder hollow chamber, 16... Valve body, 16a
...Through hole, 17a, 17b...Spring, 1
8,19...Spring seat.

Claims (1)

[Scope of utility model registration request] The flow path has an inlet flow path and an outlet flow path which are curved by a partition wall provided inside, and further has an axis arranged at a certain angle with respect to the axis of the inlet flow path. A stop valve type valve body having a hollow chamber located between the passages, provided within the valve body, communicating the inlet passage and the hollow chamber, and having an inner circumferential surface whose diameter decreases from the downstream side to the upstream side. an opening having a shaped shape, a lid attached to the valve body, a spindle supported by the lid and having an axis that coincides with the axis of the opening and capable of moving forward and backward in the axial direction;
A cylinder that is integrally provided at the lower end of the spindle, is installed to be able to move forward and backward into the hollow chamber so as to communicate with the opening, and whose lower end sealing surface can come into contact with the valve seat of the opening. a valve body that is slidably fitted into a cylinder, has a through hole therein that communicates with the opening, is located on the same axis as the opening, and always forms an orifice between the valve body; , disposed between the valve body and the cylinder so that the valve body is biased away from the opening and the expansion and contraction actions in response to fluid pressure fluctuations are performed with a substantial time difference from each other. A constant flow valve comprising a plurality of springs with different spring constants.