JPH1130347A - Fluid control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To switch from opening to closing and vice versa at high speed and to lessen leakage. SOLUTION: This fluid control valve is provided with a partition wall 2, which includes valve ports 5ac, 5ad, 5bc, 5bd composed of a group of numerous small holes and partitions the case interior in a plurality of rooms, valve plates 6, 7, which close valve ports 5ac, 5ad, 5bc, 5bd by sliding along the partition 2 and includes valve ports 8ac, 8ad, 8bc, 8bd composed of a group of numerous small holes conforming to valve ports 5ac, 5ad, 5bc, 5bd on the partition wall 2, and a driving means which makes valve plates 6, 7 slide along the partition wall 2, and when both valve ports 5ac, 5ad, 5bc, 5bd, 8ac, 8ad, 8bc, 8bd of the valve plate, which slide by the driving means, and the partition wall 2 overlap with each other, fluid passes but when both valve ports are completely discrepant, fluid is blocked.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid control valve for changing or stopping a flow direction of a fluid or adjusting a flow rate. More specifically, the present invention provides a method for stopping the flow of a fluid or adjusting the flow rate thereof, and a flow direction of a two-system fluid, for example, a two-system flow path, in particular, a flow path for flowing exhaust gas in a regenerative alternating combustion system and a combustion air. The present invention relates to a fluid control valve suitable for use as a four-way valve for alternately switching two flow paths with a heat storage body, and a three-way valve for switching fuel.

[0002]

2. Description of the Related Art In recent years, a technology has been developed in which a considerable amount of heat is recovered from exhaust gas using a heat storage body, preheated combustion air is supplied to a furnace or the like again. For example, a heat storage type that alternately supplies combustion air to a burner and exhausts combustion exhaust gas from a combustion chamber through a heat storage body, and preheats the combustion air using heat of the combustion exhaust gas stored in the heat storage body. Burner systems have been proposed.

In such a heat storage type burner system, a fluid control valve for switching between a flow path through which high-temperature exhaust gas flows and a flow path through which low-temperature combustion air flows with respect to the heat storage body is required. Conventionally, as such a fluid control valve in a combustion system, four solenoid valves are generally employed. By selectively opening and closing four solenoid valves arranged in a double pipe, a high-temperature gas and a low-temperature gas are controlled. It is configured so that the gas flow path can be switched. However, the fluid control valve constituted by the solenoid valve requires a large number of expensive solenoid valves, which increases equipment costs. In particular, when applied to heat exchange in a combustion system, a large number of more expensive high-temperature solenoid valves are required, which increases equipment costs. In addition, since the solenoid valve for air piping is quite large, if four such valves are required, there is a problem that a considerable space is required and the piping is doubled and complicated. In addition, when switching between air and exhaust gas is frequently performed in a short time of less than one minute, the durability of the solenoid valve is uneasy.

[0004] Therefore, it is desired to switch the flow path by a single relatively simple fluid control valve. As a flow path switching means composed of a single valve, use of a 4-port fluid control valve generally called a 4-way valve or the like, that is, a 4-port directional control valve can be considered. A typical 4-port directional control valve is 4
It has a simple structure in which two adjacent two of the four ports communicate with each other by a switching valve plate that rotates in a casing having four ports to switch the flow path.

As a four-way valve, a flapper type valve as shown in FIG. 8 has been considered as having improved sealing performance. This flapper type four-way valve is
A switching valve plate 207 abuts in the rotation direction to prevent a fluid from leaking. Since the switching valve plate 207 does not require a seal between its peripheral portion and the casing, even if a gap is provided between the peripheral portion and the casing for rotation of the switching valve plate, leakage from the gap does not occur. Will not wake up. Further, even when the temperatures of the two fluids are different, a gap is provided around the switching valve plate.
There is no possibility of malfunction due to sufficient extension and escape.

Further, as a fluid control valve, the valve element is rotated in the same manner as a two-port valve or a four-port valve in which the valve element is opened and closed by a valve rod (rod) that applies a vertical displacement to a valve seat. There are three-port valves for switching the direction of fluid flow.

[0007]

However, in a general structure of a four-way valve, it is difficult to prevent leakage from a gap between a switching valve plate and a casing around the switching valve plate.
If there is a large temperature difference between the two fluids, it is necessary to provide a gap at the time of high temperature, so the amount of leak will inevitably increase, and the two flow paths will cause a short path in the valve (in the casing). There is a fear.

[0008] Also in the flapper type four-way valve, it is difficult to reduce the amount of leak than the above-mentioned general four-way valve, but it is difficult to eliminate it. A clearance is required around the shaft to allow rotation of the switching valve plate, and leakage occurs therefrom. To prevent this, an expensive seal mechanism is required for the shaft. In particular, when the temperature difference between the two fluids is large and one is at a high temperature, sealing is difficult and the sealing mechanism becomes expensive.

In addition, it is necessary to simultaneously close two corresponding valve ports by rotating one valve plate in the normal and reverse directions. However, the partition wall and the valve plate are precisely and flatly processed and their positional relationship is determined. There is a problem that it is difficult to output accurately and a leak amount increases. In particular, when a high-temperature fluid and a low-temperature fluid alternately flow, the amount of leakage increases with deformation due to a temperature difference.

For this reason, the leak amount of the conventional two-port valve is about 1% or less, whereas the leak amount of the conventional four-way valve may reach 20 to 30%. In addition, since the closing accuracy of the two valve ports does not always match, there is a problem that the amount of leak differs each time switching is performed, and the flow rate fluctuates before and after switching. Further, since all ports are opened at the same time at the time of switching, a short path occurs between the two flow paths or a sudden pressure fluctuation occurs.

For this reason, when used in, for example, a regenerative burner system, the combustion air constantly leaks to the exhaust gas flow path side in the four-way valve, and the amount of the leak is not constant and unknown, so Disadvantage is that it cannot be controlled accurately. Also, every time switching is performed, there is a sudden change in the furnace pressure due to a short path. Further, when a sealing mechanism is provided, a greater driving force is required due to the friction.

In addition, a large rotational power is required due to the structure in which the valve port is pressed by a valve plate to which a rubber packing is attached to close the valve port. That is, the size of the motor, actuator, and the like, which are the driving sources, increases.

[0013] In addition, one large valve plate can be rotated 90 °.
The opening and closing are performed by rotating in the normal and reverse directions within the range, so that the movement and stroke of the valve plate required for switching are large, and the switching time cannot be shortened. That is, the structure is not suitable for high-speed switching of the flow path, such as once a second or several times a second. Further, since the stroke of the valve plate at the time of switching is proportional to the size of the valve, there is an inconvenience that the same driving device cannot be used if the size of the valve changes.

In a conventional two-port valve that opens and closes a single valve port with a valve body that moves in a direction perpendicular to the valve seat, it is difficult to grasp the outflow coefficient when the valve is slightly opened, so that it is not accurate. It is difficult to adjust the flow rate.

Further, the three-way valve, like the four-way valve, has a problem of leakage and a problem that the switching time cannot be shortened.

An object of the present invention is to provide a fluid control valve capable of switching between open and closed at a high speed and having a small leak amount. Another object of the present invention is to provide a fluid control valve capable of performing a flow path switching operation at high speed. Further, the present invention provides
It is an object of the present invention to provide a fluid control valve having a simple structure and having no fluid leakage between two flow paths, particularly two flow paths having a temperature difference.

[0017]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention is directed to a fluid control valve for changing the direction, stopping or adjusting the flow rate of a fluid flowing through a casing. A partition wall having a group of valve ports and dividing the inside of the casing into a plurality of chambers, and a group of a large number of small holes that slide along the partition walls to close the valve ports and match the valve ports of the partition walls. A valve plate having a valve port, and driving means for sliding the valve plate along the partition wall.When both valve ports of the valve plate and the partition wall slid by the driving means overlap with each other, a fluid flows. The valve is shut off when it passes and both valve ports are completely displaced.

Therefore, as shown in FIG. 3, the valve port formed by a group of a plurality of fine holes is opened and closed by the valve plate sliding along the partition wall, so that it is at least as large as the size of the holes. Is applied to the valve plate to open and close the valve.

In addition, since the stroke of the valve plate is very small, the partition wall and the valve plate can always be pressed by the urging means without losing the parallelism. Therefore, it is possible to increase the sealing performance between the partition wall and the valve plate while keeping the movement of the valve plate smooth, thereby reducing the leak and almost eliminating the leakage of the fluid. Moreover, even if a leak occurs, the amount does not change before and after the switching, and the flow rate balance after the switching is stabilized.

In addition, since the valve port is composed of a large number of small holes, the change in the flow path area immediately before closing or immediately after opening is gradual, and there is no accompanying pressure fluctuation.

In the fluid control valve according to the second aspect of the present invention, the casing is partitioned into four chambers by a substantially X-shaped partition wall, and two opposed chambers are fixed in the flow direction of the fluid. A fixed chamber connected to the two flow paths and the other two opposing remaining chambers as switching chambers connected to the two flow paths in which the flow direction of the fluid is alternately switched;
A valve port composed of a group of a large number of small holes communicating the two chambers adjacent to the partition wall is provided, while two of the four chambers slide along the partition wall to close the valve port and to close the valve port. A valve plate having a valve port composed of a group of a number of small holes, each of which is provided with a drive means for sliding the valve plate along the partition wall, and a valve plate and a partition wall which are slid by the drive means. The two adjacent chambers whose both valve ports coincide with each other communicate with each other so that the fluid passes therethrough and the two adjacent chambers whose both valve ports are completely displaced are shut off. Therefore, by the reciprocating sliding of the valve plate, the flow directions of the two fluids can be switched alternately without causing a short path.

In the fluid control valve according to the present invention, the casing is divided into three chambers by a substantially Y-shaped partition wall, and one of the chambers has a flow path in which the flow direction of the fluid is fixed. The two fixed chambers are connected to each other and the remaining two chambers are set as switching chambers connected to two flow paths in which the flow direction of the fluid is alternately switched, and these two chambers are provided on a partition wall between the fixed chamber and the two switching chambers. A valve port comprising a group of a number of small holes communicating the chambers is provided, while a valve port comprising a group of a number of small holes which slides along the partition wall to close the valve port and coincides with the valve port of the partition wall. A driving means for arranging a valve plate having a valve plate and sliding the valve plate along the partition wall, and switching either one of a fixed chamber in which both valve ports of the valve plate and the partition wall sliding by the driving means overlap each other. Fluid flows through selective communication with the chamber and both valve ports are completely displaced. The other switching chamber and are to be cut off from. Therefore, one of the two switching chambers and the fixed chamber are selectively connected by the reciprocating sliding of the valve plate, and the flow direction of the fluid is switched.

Further, in the fluid control valve according to any one of claims 1 to 3, the valve plate has two sides which are in sliding contact with two adjacent walls of the partition wall at the same time, and a valve port provided on each side. Are shifted from each other by a half pitch, and when the valve port on one side of the valve plate and the valve port on the partition wall overlap and open, the valve port on the other side and the valve port on the partition wall are shifted and closed. It is provided so that. In this case, the movement of one valve plate closes one of the two valve ports that connect the one fixed chamber and the two switching chambers, and simultaneously opens the other valve port.

Further, in the fluid control valve according to any one of the first to third aspects, the valve plate includes a plurality of plates that are in sliding contact with the corresponding walls of the partition wall, and slides individually for each valve plate. It is preferable to be provided as follows. In this case, since the valve plate with the valve port open and the valve plate with the valve port closed can be controlled separately, it is necessary to flow the fluid or change the direction after all the valve ports are closed. Only necessary valve openings can be opened.

Further, in the fluid control valve according to any one of the first to fifth aspects, it is preferable that the driving means reciprocally drive the valve plate at a high cycle. In this case, high-speed switching is realized.

Further, in the fluid control valve according to any one of the first to sixth aspects, it is preferable that the entrance of the valve port is rounded. In this case, since the pressure loss is small and the fluid easily flows, the flow is hardly disturbed.

[0027]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The structure of the present invention will be described below in detail with reference to an embodiment shown in the drawings.

FIGS. 1 to 4 show an example in which the fluid control valve according to the embodiment of the present invention is applied to a four-way fluid control valve. This four-way fluid control valve partitions the inside of the casing 1 into four chambers 3a, 3b, 3c, 3d by a substantially X-shaped partition wall 2, and two chambers arranged in a positional relationship such that they are not adjacent to each other, such as the chamber 3a. 3b is the first and second fixed chambers connected to two flow paths in which the flow direction of the fluid is fixed, and the remaining two chambers, for example, the chambers 3c and 3d, are alternately switched in the flow direction of the fluid. The first and second switching chambers are connected to two channels. The adjacent two chambers 3a and 3c, 3a and 3d, 3
The valve ports 5ac, 5ad, 5bc, 5bd are formed of a group of a large number of small holes respectively connecting the b and 3c, 3b and 3d, and the four chambers 3a, 3b, 3c, 3d are communicated next to each other. ing. In addition, two of the four chambers in the casing 1 divided into four chambers by the partition wall 2 include the partition wall 2.
The valve plates 6 and 7 are provided which slide along and close the valve ports 5ac, 5ad, 5bc and 5bd. The valve plates 6 and 7 are provided with a large number of small valve ports 8ac, 8bc, 8ad and 8bd that match the valve ports 5ac, 5ad, 5bc and 5bd of the partition wall 2. A drive means (not shown) for sliding these valve plates 6 and 7 along the partition wall 2 is provided. The valve plates 6 and 7 slid by the driving means and the two valve openings 5ac of the partition wall 2 are provided.
Two adjacent chambers in which 5ad, 5bc, 5bd, 8ac, 8ad, 8bc, and 8bd overlap are provided so as to communicate with each other and allow a fluid to pass therethrough.

Each valve port 5ac, 5 provided in the partition wall 2
The ad, 5bc, and 5bd are composed of a large number of small-diameter holes, and are provided in large numbers so as to obtain a necessary flow path cross-sectional area as a whole. The small-diameter valve ports 5ac, 5ad, 5bc, and 5bd are arranged at a constant pitch, and are provided so as to control the flow of the fluid by stopping or flowing by sliding with a half stroke of the pitch. I have. For example, FIG.
As shown in the figure, the valve ports 5ac, 5ad, 5bc, 5bd are arranged vertically and horizontally, and are formed in the sliding direction of the valve plates 6, 7, that is, in the vertical direction (arrow direction) in the present embodiment. They are arranged at a constant pitch. Further, each of the valve ports 8ac, 8bc, and 8c formed in the valve plates 6 and 7 slid along the partition wall 2.
8ad, 8bd are also formed at the same pitch as the valve ports 5ac, 5ad, 5bc, 5bd of the partition wall 2. Then, by sliding the valve plates 6 and 7 at a stroke of half the pitch described above, the valve ports 5ac, 5ad, 5bc and 5bd of the partition wall and the valve plates 6 and 7 are moved.
The valve ports 8ac, 8bc, 8ad, and 8bd are overlapped with each other to allow the fluid to pass therethrough, or to be shifted so as to stop the flow.

Each of the valve plates 6 and 7 and the partition wall 2 are slidably pressed against each other by, for example, elastic force of a spring or suction by a magnet, and are brought into close contact with each other. Here, the stroke of the valve plate is extremely short and minute. For example, in the case of this embodiment, it is in the range of about 0.5 mm to 1 mm. Therefore, as shown in FIG. 1, even if biasing means such as a compression coil spring 4 is interposed between the casing 1 and the valve plates 6 and 7, the effect of the displacement of the valve plates 6 and 7 on the spring 4 is not affected. Almost negligible. Therefore, even if the valve plates 6 and 7 are pressed against the partition wall 2 by the spring 4, the movement of the valve plates 6 and 7 is not hindered, so that the leakage can be extremely reduced and the leakage can be suppressed to about several percent or less. In addition, since the strokes of the valve plates 6 and 7 are extremely small, the valve plates 6 and 7 do not need to be entirely flat. Even if the valve plates 6 and 7 are curved or deformed in a range larger than the stroke, the parallelism is high. Will not be lost.
The spring 4 is formed on the casing 1 and the valve plates 6 and 7 with a seat surface or the like as necessary, and is stably held. In the case where the magnets are attracted by magnets, magnets having opposite polarities are embedded in the surfaces of the valve plates 6 and 7 and the partition wall 2 facing each other, and are attracted. The method of pressing each of the valve plates 6 and 7 against the partition wall 2 is not particularly limited to the above-described method. For example, a tension spring is built in a surface of the valve plates 6 and 7 facing the partition wall 2 so that the valve plates 6 and 7 are connected to each other. The partition wall 2 may be provided so as to pull each other.

Here, the valve plate 6 provided with the valve ports 8ac and 8ad and the valve plate 7 provided with the valve ports 8bc and 8bd form an L-shape, and the one fixed chamber 3a or 3b is moved by one movement. The valve ports 8ac, 8ad, 8bac, 8b of the valve plates 6, 7 are selectively connected to the two switching chambers 3c or 3d communicating with the valve chambers.
The relationship between d and 5ac, 5ad, 5bc, 5bd has been determined. That is, the movement of the valve plate 6 causes one valve port, for example, 8ac.
When the fixed chamber 3a and the switching chamber 3c communicate with each other so that the fixed chamber 3a and the switching chamber 3c communicate with each other, the other valve ports, for example, 8ad and 5ad are displaced, so that the fixed chamber 3a and the switching chamber 3d are shut off, and the valve plate 6 is moved in the opposite direction. When the valve chambers 8ad and 5ad move and the fixed chamber 3a and the switching chamber 3d communicate with each other, the other valve ports 8ac and 5ac are displaced and the fixed chamber 3a and the switching chamber 3c are shut off. Have been. The same applies to the arrangement relationship between the valve openings 8bc and 8bd of the valve plate 7 and the valve openings 5bc and 5bd of the partition wall 2. One movement of the valve plate 7 causes one fixed chamber 3b and two switching chambers 3 to move.
To selectively communicate with either c or 3d,
Due to the movement of the valve plate 7, one of the valve ports, for example, 8bc and 5bc overlaps, and the fixed chamber 3b and the switching chamber 3c communicate with each other, and the other valve port, for example, 8bd and 5bd shifts and the fixed chamber 3b and the switching chamber 3d are shifted.
Is shut off. Here, the valve plate 7
And the valve plate 6 are set to an opening and closing operation such that they are simultaneously moved in the same direction in synchronization with each other. However, the opening and closing operation is not particularly limited thereto. The plates 6 and 7 may be switched in the opposite direction by operating them.

The valve openings 5ac, 5ad, 5b of the partition wall 2 are also provided.
The c, 5bd and the valve openings 8ac, 8ad, 8bc, 8bd of the valve plates 6, 7 may be abutted by a simple flat plate contact. It is preferable to configure so as to also serve as a guide in the sliding direction. For example, as shown in FIG. 4 exemplifying the valve plate 6, a cylindrical projection 10 is formed around a valve port 8 ad on the valve plate 6 side, and the projection 10 of the valve plate 6 is fitted on the partition wall 2 side. A rectangular groove having a width to be drawn and a length corresponding to a stroke in the sliding direction (FIG. 4)
11B, the groove 11 and the projection 10 guide the valve plate 6 in the sliding direction and regulate the stroke end. The groove 11 is not limited to a rectangular shape, and may be, for example, an elliptical groove as shown in FIG. In short, it has a length corresponding to the stroke of each valve plate 6, 7 in the sliding direction of the valve plate 6, 7,
A groove or the like that forms a minimum gap that does not hinder sliding in the width direction is sufficient.

Each valve port 5ac, 5ad, 5bc, 5bd, 8ac, 8a
As shown in FIG. 4, roundness 12 is formed at the entrances of d, 8bc, and 8bd. This prevents turbulence from occurring in the flow of the passing fluid and reduces the pulsating flow.

Further, the first and second fixed chambers 3a, 3b
The first and second switching chambers 3c and 3d are provided with ports 9a, 9b, 9c and 9d for connecting the flow paths one by one. And the first and second fixed chambers 3
Two flow paths (ducts) in which the flow direction of the fluid is fixed are respectively connected to a and 3b, and the flow direction of the fluid is alternately switched to the first and second switching chambers 3c and 3d. The flow paths (ducts) of the system are connected.

As a driving means for reciprocating the valve plates 6 and 7 along the partition wall 2, an element, a control device, and a mechanism capable of generating a minute stroke can be used. For example, vibration of an electromagnetic coil or a piezoelectric element can be used. It is preferable to use an element, a tappet cam driven by a motor, or the like, and most preferable to use a vibration element such as an electromagnetic coil capable of switching a minute stroke at a high cycle. Although not shown, the driving means is generally provided outside the casing 1 and a rod or the like for transmitting the movement penetrates into the casing 1 and is connected to the valve plates 6 and 7. The driving means is provided for each valve plate, but is not limited to this, and each of the valve plates 6 and 7 may be driven by one common driving means.

The flow path switching by the fluid control valve thus configured is performed as follows. This operation will be described in connection with a case in which the flow direction of two fluids, that is, an air supply system and an exhaust system, is alternately switched in a heating furnace or the like using a heat storage type alternating combustion system in which the flow directions are reversed as a heat source.

For example, low-temperature combustion air as a supply fluid flows into the first fixed chamber 3a, while the second fixed chamber 3b
Exhausts high-temperature combustion exhaust gas as an exhaust fluid. In the state shown in FIG. 1, the fluid introduced into the first fixed chamber 3a flows into the first switching chamber 3a through the valve port 8ac of the valve plate 6 and the valve port 5ac of the partition wall 2, and is connected to the same chamber 3b. Is supplied via a duct to a regenerator (not shown). On the other hand, the second
An exhaust duct including an induction fan is connected to the fixed chamber 3b. Then, similarly to the second switching chamber 3c, a heat storage body (not shown) is connected via a duct. The heat storage body connected to the second switching chamber 3d and the first
Is different from the heat storage element connected to the switching chamber 3c, or is a different part of the same heat storage element. The combustion system is configured to alternately supply and exhaust air through these heat storage bodies. Therefore, the combustion exhaust gas induced via the heat storage element connected to the second switching chamber 3d is introduced into the second switching chamber 3c, and thereafter, the valve port 5bd of the partition wall 2 and the valve port 8bd of the valve plate 7 are provided. Through the second fixed chamber 3b, and then discharged to the exhaust system. At this time, the first fixed chamber 3
a, the valve port 8ad of the valve plate 6, the valve port 5ad of the partition wall 2 and the second port.
8bc of the valve plate 7 of the fixed chamber 3b and 5bc of the partition 2
Since the valve plates 6 and 7 and the partition wall 2 overlap with each other, the combustion air and the exhaust gas do not mix with each other.

Next, when an actuator (not shown) such as a vibrator is driven and slid in the opposite direction from the state shown in FIG. 1, the valve plates 6 and 7 slide along the partition wall 2, and the valve plates 6 and 7 slide in the opposite direction. The valve port 8ad of the valve plate 6 of the first fixed chamber 3a and the valve port 5ad of the partition wall 2 and the valve port 8bc of the valve plate 7 of the second fixed chamber 3b and the valve port 5bc of the partition wall 2 respectively overlap. In this manner, the first fixed chamber 3a and the switching chamber 3d are communicated with each other, and the second fixed chamber 3b and the switching chamber 3c are communicated with each other, and the fluid flowing into the first fixed chamber 3a from the port 9a, for example, for combustion. The air flows into the second switching chamber 3d from the valve port 5ad, and is supplied to the flow path connected to the port 9d. On the other hand, from the port 9b, exhaust fluid, for example, combustion exhaust gas, which is drawn into the first switching chamber 3c via the port 9c, is discharged from the valve ports 8bc and 5bc through the second fixed chamber 3b.

The switching of the flow path by the fluid control valve constructed as described above is performed by dividing the four chambers in the casing 1 completely by the substantially X-shaped partition wall 2 and by sliding the valve plates 6 and 7 together. Since it is sealed by the close contact with the wall 2, gas leakage does not occur between the two flow paths in the casing.

FIG. 5 shows another embodiment. This embodiment is applied to a three-port valve, and is suitable for use as a switching valve of a fuel supply system of a regenerative alternating combustion system. The three-way fluid control valve includes three chambers 23a, 23a,
23b and 23c, one of which is, for example, the room 32
a is a fixed chamber to which a flow path in which the fluid flow direction is fixed is connected, and the remaining two chambers 23b and 23c are connected to two flow paths in which the flow direction of the fluid is alternately switched. And The partition wall 22 between the fixed chamber 23a and the switching chambers 23b and 23c is provided with valve ports 25ab and 25ac each formed of a group of a large number of small holes for communicating these two chambers, respectively. A valve plate 26 which slides along and closes the valve ports 25ab and 25ac and has a group of a number of small holes matching the valve ports 25ab and 25ac of the partition wall 22 and has valve ports 28ab and 28ac is arranged. The valve plate 26 is driven to reciprocate along the partition wall 2 by driving means (not shown). Then, the fixed chamber 23 in which the valve plate 26 slid by the driving means and the two valve ports 25ab, 25ac, 28ab, 28ac of the partition wall 22 overlap.
a and one of the switching chambers 23b or 23c is selectively communicated to allow a fluid to flow, and the other switching chamber 23c or 23b in which both valve ports are completely displaced and the fixed chamber 23a are shut off.

This three-port fluid control valve is different from the four-port fluid control valve shown in FIGS. 1 to 4 in that the partition wall structure is Y-shaped and the casing is divided into three chambers. The only difference is that the mode is switched to either one, and the other configurations are the same.

FIG. 6 shows still another embodiment. This embodiment is applied to a two-port valve and can be used as a flow control valve or a directional control valve, and is particularly suitable for use as a fuel supply valve in a regenerative alternating combustion system. is there. This fluid control valve has a valve port 35 composed of a group of a large number of small holes, and a partition wall 3 that partitions the inside of a casing 31 into two chambers 33a and 33b.
2, a valve plate 36 which slides along the partition wall 32 to close the valve port 35 and has a valve port 38 comprising a group of a number of small holes which coincide with the valve port 35 of the partition wall 32; 36
And a driving means 39 for sliding the valve plate 36 along the partition wall 32.
The fluid flows through the casing 31 by shutting off the fluid when the two valve ports 35 and 38 overlap with each other and when the two valve ports 35 and 38 are completely displaced. Here, reference numeral 40 in the drawing denotes a rod for transmitting the movement of the vibrator 39 as a driving means to the valve plate 36, and is connected to the valve plate 36. A pulse power supply 42 is applied to the vibrator 39 as a driving means, and the valve is opened and closed at a desired frequency.

Further, by making the movement of the driving means arbitrarily adjustable, the opening of the valve plate can be adjusted by, for example, adjusting the rotation angle of the motor or controlling the frequency of the current applied to the electromagnetic coil or the piezoelectric element. Is also good. Thereby, the opening degree of the valve port is fixed at an arbitrary position, and a flow control valve in which the flow rate of the passing fluid is controlled to an arbitrary flow rate can be configured. In this case, since the stroke of the valve plate is short, the flow rate control is performed quickly and the response is extremely high. This valve can be used as a fuel control valve or other fluid flow control valve. In this case, since the valve is opened and closed with a small displacement, the driving means is applied intermittently at a high cycle by applying a driving voltage or current which changes at a high cycle to a vibrator or an electrostrictive element as the driving means. Can be supplied to Also, instead of rapidly opening and closing a single large valve port like an electromagnetic valve, a flow path required by a number of sufficiently small holes (for example, about 1 mm in diameter) constituting the valve ports 35 and 38 is required. Since the cross-sectional area is obtained and the opening and closing of each fine hole is performed, the amount of the passing fluid gradually increases or decreases with the opening and closing of the valve. Therefore, when used as a fuel supply valve in a regenerative alternating combustion system, the combustion at the time of switching gradually increases and decreases gradually, so that the pressure fluctuation in the furnace does not become abrupt. Furthermore, when configured as a flow control valve, since the outflow coefficient of each valve port can be completely predicted, the flow rate can be accurately estimated if the shape of each valve port is accurately processed, so that an accurate flow rate can be obtained. Control becomes possible. In particular, if the inlets and outlets of each valve port are rounded, the outflow coefficient reaches up to about 0.9, the flow is easy to flow, the pressure loss is small, the flow rate can be controlled more accurately, and the pressure fluctuation is small. In this state, a flow control valve with good responsiveness and response in which the flow rate changes immediately according to the movement of the valve plate can be realized.

Each of the fluid control valves configured as described above
For example, as a switching means / four-way valve for alternately connecting the exhaust system and the air supply system of the regenerative burner system to the regenerator, or as a three-way valve for alternately supplying fuel to a pair of burners,
Further, it is suitable as a fuel injection valve, a fuel supply valve or a fuel regulating valve, but is not particularly limited to these uses, and can be used for all kinds of fluids such as a general flow regulating valve, a directional control valve, and a shutoff valve. It goes without saying that the present invention can be implemented as a target fluid control valve.

Although each of the above embodiments is one of the preferred embodiments, the present invention is not limited thereto, and various modifications can be made without departing from the gist of the present invention.
For example, in the present embodiment, one valve plate is provided so as to open and close the valve ports facing the two switching chambers at the same time. However, the present invention is not particularly limited to this, and a valve is provided for each valve port comprising a group of small holes. A plate may be provided so that it can be individually opened and closed. That is, as shown in FIG.
An actuator 6 is provided for each of the valve plates 6 and 6 'so as to be individually driven. In this case, the opening and closing of each valve port 5ad, 5ac, 5bd, 5bc can be controlled by shifting the drive timing of the actuator, so that each valve port 5ad, 5ac, 5bd, 5bc of the partition wall 2 and each valve port of the valve plate. 8
The positional relationship between ad, 8ac, 8bd, and 8bc is not limited to the above-described embodiment. Each valve port 5ad, 5 with exactly the same positional relationship
Even when the ac, 5bd, 5bc and the valve ports 8ad, 8ac, 8bd, 8bc are arranged, an arbitrary opening / closing operation can be obtained by controlling the drive timing and the drive direction of each valve plate 6, 6 'by the actuator. Can be Therefore, in some cases, after the valve ports 5ad, 5ac, 5bd, and 5bc are fully closed, the two valve ports can be simultaneously opened or sequentially opened so as to communicate with an arbitrary switching chamber. For example, the two valve ports that have been open up to that time may be closed simultaneously or sequentially to close all the valve ports, and then the valve ports to be opened next may be opened simultaneously or sequentially to switch the fluid flow. . That is, by operating the valve port in the order of closing → closing → opening → opening, it is possible to suppress a short path or pressure fluctuation between the two flow paths. Therefore, when this valve is used as a means for switching between combustion air and exhaust gas in an alternating combustion system, the burden on the furnace body can be reduced. Also, in the case where it is preferable to perform exhaust prior to air supply, for example, after fully closing the valve port, first open the valve port that communicates one of the switching chambers and the fixed chamber to which the exhaust system is connected, Thereafter, a valve port for communicating the other switching chamber with the fixed chamber to which the air supply system is connected may be opened next.

In this embodiment, each port 9a, 9
The description has been made on the assumption that one flow path is connected to each of b, 9c, and 9d. However, the present invention is not particularly limited to this. The road may be connected to one port.
In short, as long as one channel is connected to one chamber, the number of channels may be plural.

Further, in the present embodiment, a description is mainly given of a relatively high-temperature gas and a low-temperature gas as examples of the two systems of fluids, but the present invention is not particularly limited to this, and cooling energy can be reduced. The present invention can also be used for changing the flow path between a fluid having the same temperature and a normal temperature fluid, and for switching a flow path between two fluids having different physical properties without a temperature difference. It may be used in a circulation system or the like used for processing gas containing odors, toxic components, and the like, in which leakage to the outside of the system is not preferable or must be completely avoided.

Further, in this embodiment, two systems in which the directions of flow of the fluid are fixed are described as two systems in which the flow directions are opposite, such as an air supply system and an exhaust system, but the invention is not limited to this. Instead, two systems in which fluid flows in the same direction may be used.

Further, in this embodiment, the valve ports 5ac, 5a
Each of d, 5bc, 5bd and 8ad, 8ac, 8bd, 8bc is constituted by a single circular hole, but is not particularly limited thereto. It may be a hole other than a circle, for example, a hole such as a square or a triangle, or the valve openings of the valve plates 6, 7 and the partition wall 2 may be made different. The shapes of the valve ports of the plate or the partition wall may be different from each other. In addition, even if there are many holes simultaneously opened and closed by one valve plate, it is recognized as one valve port as a whole.

Further, in the present embodiment, each valve port 5ac, 5ad, 5bc, 5bd of the partition wall 2 and each valve port 8ad, 8ac,
Although 8bd and 8bc are formed in the same size and a perfect circle at a constant pitch, the present invention is not particularly limited to this, and one of them may have a large diameter or a hole shape different from each other. Further, fine valve openings formed on the same wall surface or side surface may be formed, for example, with different pitches at the same pitch, or conversely, with different pitches formed at the same pitch. You may. Furthermore, the combination of holes is not particularly limited, and one valve port may be round and the other valve port may be elliptical, polygonal, triangular, rectangular, or the like. For example, a part of the valve port of the valve plate or the partition wall is made larger in diameter than the corresponding counterpart valve port, and when this large-diameter valve port is completely displaced from the counterpart valve port, The fuel control valve may be formed at a pitch such that the valve port is closed. In the case of the conventional flow control valve used for the fuel supply system, there is a problem that the furnace pressure fluctuates too much when ignited because a large amount of fuel is suddenly injected, but large and small diameter valve ports are mixed. In the case of the above-described flow control valve, the opening change immediately after opening and immediately before closing is gradual even with the same stroke, and the fuel injection amount is gradually increased or decreased to reduce the furnace pressure fluctuation at the time of ignition or misfire. Can be.

[0051]

As is apparent from the above description, according to the fluid control valve according to the first, second, and third aspects,
Since the valve port formed by a group of a plurality of fine holes is opened and closed by the valve plate sliding along the partition wall, the valve can be opened and closed by moving a small valve plate at least as much as the size of the hole. The switching time can be shortened. Therefore, high cycle switching is possible.

Further, since the stroke of the valve plate is very small, the partition wall and the valve plate can always be pressed by the urging means without losing the parallelism. Therefore, it is possible to increase the sealing performance between the partition wall and the valve plate while keeping the movement of the valve plate smooth, thereby reducing the leak and almost eliminating the leakage of the fluid. Therefore, the flow rate balance after switching is also stabilized.

Further, since the stroke for opening and closing depends on the size of the valve port, regardless of the size of the valve, the stroke can be the same regardless of the size of the valve.
The same driving means can be used even when the valve diameters are greatly different.

Further, since the valve port is composed of a large number of small holes, the flow area immediately changes immediately before closing or immediately after opening, so that the flow rapidly changes and large pressure fluctuation occurs. Nothing.

Further, according to the fluid control valve of the second aspect, switching of the flow direction of the two systems of fluid can be realized without causing a short path. In addition, even if there is a temperature difference between the two fluids, the influence of possible deformation of the valve plate and the like caused by the temperature difference hardly causes a problem because the stroke of the valve plate is minute, and the durability is remarkably higher than the conventional one. Can improve. For this reason, when applied to direct heat exchange using a heat storage material such as a regenerative alternating combustion system, the temperature efficiency can be maximized and the volume of the heat storage material can be reduced.

According to the fluid control valve of the third aspect, the switching of the flow direction of a single fluid can be realized at high speed without leakage.

Further, according to the fluid control valve of the fourth aspect, one of the two valve ports for communicating one fixed chamber and two switching chambers by closing one valve plate by moving one valve plate is closed at the same time as the other valve. The mouth can be opened and the switching time can be further reduced. At this time, a state where the fixed chamber and the two switching chambers are simultaneously opened occurs. However, since the stroke of the valve plate is minute, it is an instant which is negligibly short as compared with that of the conventional four-way valve. Since the stroke of the valve plate for opening and closing is the same regardless of the size of the valve, there is substantially no problem.

Further, according to the fluid control valve of the fifth aspect, the valve plate with the valve port open and the valve plate with the valve port closed can be controlled separately, so that all the valve ports are closed. After that, only the necessary valve openings can be opened to allow the fluid to flow or turn. Therefore, unlike the conventional type, they are not opened at the same time, the pressure fluctuation at the time of switching can be reduced, and the short path of the fluid between the two flow paths can be prevented.

According to the fluid control valve of the sixth aspect, since the valve plate can be reciprocated at a high cycle, high-speed switching which cannot be realized by a conventional fluid control valve such as an electromagnetic valve or a rotary four-way valve, for example, once per second, can be achieved. Short-time switching such as several times or tens or hundreds of times per second can be realized. For this reason, in an alternating combustion system or the like using a heat storage element, the switching time can be reduced as much as possible in order to increase the temperature efficiency.
This is not limited to the alternating combustion system, but can be used for all types of regenerative heat exchangers that exchange heat by flowing fluids having different temperatures through the regenerator. Can be reduced as much as possible.

According to the fluid control valve of the present invention, the pressure loss is small because the entrance and exit of the valve port are rounded. A flow control valve with good responsiveness and responsiveness can be realized in which the flow is easy and the pressure loss is small, the flow rate can be controlled more accurately, and the flow rate changes immediately according to the movement of the valve plate in a state where the pressure fluctuation is small. Since the outflow coefficient of each valve port can be completely predicted, the outflow amount can be accurately estimated if the shape of each valve port is accurately processed, so that accurate flow rate control can be performed.

[Brief description of the drawings]

FIG. 1 is a central longitudinal sectional view showing in principle an example of an embodiment in which a fluid control valve of the present invention is applied to a four-way valve.

FIG. 2 is a perspective view of a valve plate used for the four-way valve of FIG.

FIGS. 3A and 3B are front views showing a relationship between a partition wall and a switching valve plate of the fluid control valve of FIG. 1, wherein FIG. 3A shows an open state and FIG.

4A and 4B are diagrams showing an example of a structure of a valve port portion between a partition wall and a valve plate, wherein FIG. 4A is an enlarged vertical sectional view, FIG. 4B is a front view showing an example thereof, and FIG. It is a front view showing an embodiment.

FIG. 5 is a central longitudinal sectional view showing in principle an example of an embodiment in which the fluid control valve of the present invention is applied to a three-way valve.

FIG. 6 is a central longitudinal sectional view showing in principle an example of an embodiment in which the fluid control valve of the present invention is applied to a two-port valve / flow control valve.

FIG. 7 is a perspective view showing another embodiment of the valve plate.

FIG. 8 is a schematic view showing a conventional flapper valve.

[Explanation of symbols]

 1, 21, 31 Casing 2, 22, 32 Partition wall 3a, 23a, 33a First fixed room 3b Second fixed room 3c First switching room 3d Second switching room 5ac, 5ad, 5bc, 5bd, 25ac , 25ab, 35 Valve port 6, 6 ', 26, 36 Valve plate 7 Valve plate 8ac, 8ad, 8bc, 8bd, 28ac, 25ab, 38 Valve port

Claims (7)

[Claims] 1. A fluid control valve for changing, stopping, or adjusting a flow rate of a fluid flowing in a casing, a partition having a valve port composed of a group of a large number of small holes and dividing the interior of the casing into a plurality of chambers. A valve plate having a wall, a valve port comprising a group of a number of small holes sliding along the partition wall to close the valve port and to match the valve port of the partition wall; and A drive means that slides along the valve, and when both valve ports of the valve plate and the partition wall that slide by the drive means overlap with each other, the fluid passes and both valve ports are completely displaced. A fluid control valve that is shut off. 2. The casing is divided into four chambers by a substantially X-shaped partition wall, and two opposing chambers are fixed chambers connected to two flow paths in which the flow direction of the fluid is fixed. And the other two opposing chambers are switching chambers connected to two flow paths in which the flow direction of the fluid is alternately switched, and a group of a large number of small holes communicating the two chambers adjacent to the partition wall. And a valve comprising a group of a large number of small holes that slide along the partition wall to close the valve port and match the valve port of the partition wall in two of the four chambers. A drive means for arranging valve plates each having a port and sliding the valve plate along the partition wall, wherein the valve plate slid by the drive means and the valve ports of the partition wall are adjacent to each other. The two chambers communicate and the fluid passes and both valve ports are not completely A fluid control valve, wherein two adjacent chambers are shut off. 3. The casing is divided into three chambers by a substantially Y-shaped partition wall, and one of the chambers is a fixed chamber to which a flow path having a fixed fluid flow direction is connected, and the remaining two chambers are connected. A switching chamber connected to two flow paths in which the flow direction of the fluid is alternately switched, and a group of a large number of small holes that communicate these chambers with the partition wall between the fixed chamber and the switching chambers. While providing a valve port, the valve plate is provided with a valve port comprising a group of a large number of small holes that slide along the partition wall to close the valve port and match the valve port of the partition wall, Driving means for sliding a valve plate along the partition wall is provided, and the valve chamber slid by the driving means, the fixed chamber in which both valve ports of the partition wall overlap, and one of the switching chambers are selected. The fixed chamber in which fluid flows and the valve ports are completely displaced And the other switching chamber is shut off. 4. The valve plate has two sides that are in sliding contact with two walls adjacent to the partition wall at the same time, and the valve ports provided on each side are shifted from each other by a half pitch, so that one of the valve plates has one side. The valve port of the other side and the valve port of the partition wall are shifted and closed when the valve port of the side overlaps with the valve port of the partition wall to open the valve. The fluid control valve according to any one of the above. 5. The valve plate according to claim 1, wherein the valve plate includes a plurality of plates that are in sliding contact with the corresponding walls of the partition wall, and each valve plate slides individually. Fluid control valve. 6. The fluid control valve according to claim 1, wherein the driving unit drives the valve plate to reciprocate at a high cycle. 7. The fluid control valve according to claim 1, wherein the inlet and outlet of the valve port are rounded.