JPH04214936A - Rotary plate valve - Google Patents

Abstract

PURPOSE:To provide a rotary plate valve with which a load torque can be reduced largely in operation to be used for controlling opening/closing of a passage and flow at a middle position for automotive engine supply air systems, air conditioning devices, plant pipings, vacuum exhaust devices, etc. CONSTITUTION:A first blade 201 to move to the downstream side in opening toward a current, a second blade 202 to move to the upstream side toward the current, and a valve body comprising the first blade 201 and the second blade 202 are provide. By forming the first blade 201 in a recessed surface to receive fluid to the current, or the second blade 202 in a protruding surface to receive fluid to the current, thereby a load torque generated by unbalance of static pressures applied to both side parts of the plate-like valve body can be reduced.

Description

[Detailed description of the invention]

0001

[Industrial Application Field] The present invention is widely used for the purpose of opening/closing flow paths and controlling flow rate at intermediate positions in automotive engine air supply systems, air conditioning equipment, plant piping, vacuum exhaust systems, etc. This relates to a rotating plate type valve.

0002

2. Description of the Related Art Conventionally, rotating plate type valves have been used as air intake throttle valves for automobile engines because they have a simple structure and are easy to adjust the flow rate. Such an air intake throttle valve is configured to move mechanically with the accelerator pedal, etc. operated by the driver, so that the operating force of the driver is directly transmitted to the rotational force of the air intake throttle valve. Ta. The force required to operate the air intake throttle valve is much smaller than, for example, the force required by a human to press an accelerator pedal, so there was no difficulty in operating the air intake throttle valve.

However, in recent years, attempts have been made to view the automobile as a mechanism that integrates man and machine, and to achieve higher performance by comprehensively controlling each unit. Efforts were also made to introduce electronic control technology. In other words, the accelerator pedal and throttle, which were conventionally connected mechanically, are separated, and the throttle opening is optimally controlled according to the driver's intentions and the vehicle's driving conditions, thereby improving the sense of acceleration and driving feeling. It is. As a result, the characteristics of the throttle valve itself as a controlled object have been attracting attention as a matter of great concern because they have a great influence on the performance of the entire control system.

Regarding the flow rate characteristics of the throttle valve, there have already been proposals for improving the flow rate characteristics, such as in Japanese Patent Application Laid-Open No. 146029/1983, with the aim of finely controlling the engine output. However, improving flow characteristics alone is not enough.
Even if it becomes easy to finely adjust the flow rate in the small valve opening range, it is difficult to improve the performance of the entire control system including the throttle valve.

The present inventors focused on improving the load torque characteristics of the throttle valve. The purpose of this is to reduce the load torque on the valve, thereby improving the performance and downsizing of the throttle valve driven by a servo motor, etc., and its control system as a whole. Furthermore, the characteristics of the throttle valve (generally called a butterfly valve) have been clarified theoretically and experimentally by many researchers to date.

For example, Morris. M. J et al., peak torque characteristics of butterfly valve, Vol. 54, pp. 63-66,
1987 (Peak torque character
ristics of butterfly Valv
e VOL. 54, pp. 63-66, 1987), a detailed experimental analysis of the unbalanced torque caused by aerodynamic factors of butterfly valves was conducted. In the above research, the torque characteristics that have a maximum value at a certain valve opening are determined from the results of measuring the static pressure on the disk surface of a butterfly valve.

As an example of characteristic analysis using computer simulation, for example, Kato et al. ``Characteristic analysis of flow around a flat plate placed between two-dimensional parallel walls by numerical analysis'' {Kogakuin University Research Report No. 55 , 1983}, numerical calculations were performed using the Navie-Stokes equation and the continuity equation simultaneously in the flow field. We use numerical calculations to determine the flow state, velocity, and pressure distribution around the valve, and use these results to analyze the valve's torque characteristics.

[0008] However, all of the above-mentioned studies are based on the well-known fact that the valve has a peak torque at a certain opening degree, and are aimed at elucidating the detailed phenomena of the flow around the valve and developing methods to elucidate it. The main focus is on Therefore, the aim of the present invention is to "reduce torque."
To the best of the present inventors' knowledge, there has been no research example based on a theoretical approach from the viewpoint of "What should the valve shape be?"

[0009]

Problem to be Solved by the Invention Now, the problem with flow rate control using a throttle valve is how to position the valve quickly and accurately.
It comes down to whether you can decide the angle). If a large load torque (unbalanced torque) is generated due to fluid drag on the throttle valve, which is the load on the motor, and this load torque is largely dependent on the opening degree of the valve, it is necessary to realize a stable control system. It becomes a big obstacle.

[0010] Automotive equipment is required to be small and simple due to constraints on installation space and power supply, but small electric motors with limited drive torque can withstand high load torque and have a high-speed response. This makes highly accurate valve positioning difficult.

FIG. 23 shows the structure of a conventional general rotary plate valve, in which a valve shaft 2 is rotatably attached in the middle of a piping flow path 1, and flat plate valves are mounted on both sides of the valve shaft 2. The left and right halves 3 and 4 of the body are protruding. In the figure, a white arrow indicates the direction of flow. If the valve shaft 2 is rotated to block the flow path 1 with the flat valve bodies 3 and 4 perpendicular to the flow, the flow is blocked and the flat valve bodies 3 and 4 are rotated clockwise in the figure. If you move it, the valve will open. Figure 4 shows the relationship between the valve opening φ and the load torque T as shown by the chain line (conventional example) after analyzing the flow near the valve (the analysis conditions will be described later) in a rotating plate valve with such a structure. ). It can be seen from this graph that the load torque T has a peak value when the valve opening degree φ is around 35 degrees.

[0012] Therefore, in order to drive the intake air throttle valve consisting of a rotating plate type valve as described above with a motor, a drive motor having a capacity sufficiently exceeding the maximum value of the load torque T must be installed. This results in an increase in the size of the drive motor and an increase in power consumption and cost of the control circuit that drives the motor.

The fact that a rotating plate type valve has a large load torque due to fluid drag means that, in addition to the above-mentioned intake air throttle valve for automobile engines, rotating plate type valves with a similar structure are used in various plants, for example. This problem also occurs when a butterfly valve or the like is driven and controlled by an electric actuator.

To summarize, the object of the present invention is to provide a rotary plate valve that can significantly reduce the load torque during operation.

[0015]

[Means for Solving the Problems] A rotary plate valve of the present invention for solving the above problems includes a first blade that moves downstream when opening in the flow direction, and a first blade that moves upstream in the flow direction. a second vane, a valve body including the first vane and the second vane, a valve shaft supporting the valve body, and rotatably housing the valve body via the valve shaft, and a flow path for guiding fluid, and either the first blade has a concave surface in the flow direction and is formed in a shape to receive the fluid, or the second blade has a convex surface in the flow direction. It is characterized by being formed in a shape that receives fluid.

[0016]

[Operation] Figure 1 is a model diagram of valves of the present invention and a conventional example.
The operation of the present invention will be explained using (a) and (b).

In the conventional throttle valve shown in FIG. 1B, the valve body is composed of a first blade 101 and a second blade 102 with a valve shaft 100 as the axis, and is housed in a flow path 103. shall be. Further, the nozzles formed between the respective tips of the first blade 101 and the second blade 102 and the wall surface of the flow path 103 are connected to the first aperture 104 and the second aperture 1.
05.

Now, in the conventional valve {FIG. 1(B)}, torque is generated in the direction of closing the valve (in the direction of arrow C' in the figure), and the reason is as follows. When the blade is tilted, the flow is separated into two flows (A' and B' in the figure) toward the first and second apertures 104 and 105 on the upstream side of the flow path. Regarding the flow A' toward the first aperture 104, the fluid passage has an acute tapered shape along the direction in which the fluid advances. Due to the smoothness of the flow, the flow velocity of the fluid flowing along the upstream surface of the first blade 101 is high.

On the other hand, the flow B' toward the second opening is
Near the wall surface of the tip of the second wing 102, a major change in direction of travel is required. Therefore, the flow velocity on the upstream wall of the second blade 102 is small. From Bernoulli's theorem, if U is the flow velocity of the fluid, P is the static pressure, and ρ is the fluid density, then

[0020]

[Math 1]

[0021] Therefore, the first blade 101 with a large flow velocity U
The static pressure P on the upstream wing surface of the second wing 102 is small, and the static pressure on the upstream wing surface of the second wing 102 is large. Just as in the flow around the wings of an airplane, the difference in flow velocity above and below the wing becomes a difference in static pressure and produces lift, so also in the case of a throttle valve, the difference in flow velocity on the first and second wing surfaces becomes a difference in static pressure. , which creates a moment about the valve stem in the direction of closing the valve.

In FIG. 1(A), which is a model diagram of the present invention, the rotating plate type valve has a valve shaft 200 as its axis, and a first wing 201 formed to receive fluid with a concave surface with respect to the flow. , a second surface formed to receive the fluid with a convex surface relative to the flow.
It is composed of wings 202. The nozzles formed between the flow path 203 and the blade tip are referred to as a first aperture 204 and a second aperture 205, respectively.

Now, the effects of the present invention can be briefly explained in the scope of potential fluid dynamics as follows.

When the blades are tilted, also in the throttle valve of the present invention, two flows (A and B in the figure) flow toward the first and second openings 204 and 205 on the upstream side of the flow path.
be separated into

The flow A along the first blade surface toward the first aperture 204 is a "flow along an obtuse angle," and the flow velocity increases at the bottom of the depression, as if the wind were passing over a depression. approaches 0 (ie the static pressure is maximum).

On the other hand, a second opening 20 along the second wing surface
Flow B toward 5 is a "flow around an acute angle," and the flow velocity is maximum (that is, the static pressure is minimum) at its apex. 1st
The increase in the static pressure on the upstream side wall surface of the second blade and the decrease in the static pressure on the upstream side wall surface of the second blade simultaneously act as a moment in the direction of opening the valve (in the direction of arrow C in the figure).

Therefore, the points of view of the rotary plate valve according to the present invention can be summarized as follows: (1) It is difficult for fluid to flow along the first blade surface over a wide range of opening degrees of the valve.

(2) Fluid flows easily along the second blade surface. By selecting a similar curved shape of the valve, the static pressure difference between the first and second blade surfaces can be minimized and the torque can be reduced.

Furthermore, as can be seen from the above explanation of the operation, even if only one of the concave surfaces formed on the first blade and the convex surface formed on the second blade is formed, the conventional valve is different from the conventional valve. Since a moment is generated in the opposite direction to open the valve, the load torque can be reduced.

[0030]

Embodiments An embodiment of the present invention will be described in detail below with reference to FIG.

FIG. 2 shows an example of the valve structure of the present invention, and FIG. 3 is a sectional view taken along line AA in FIG. A valve body is composed of a first blade 20 and a second blade 30, with the valve shaft 10 as the axis, and is attached to the center of a flow path 40, which is an intake cylinder. In FIG. 3, 50 is the first opening, and 60 is the second opening.
The hole should be . In the figure, the white arrow indicates the flow direction.

Further, in FIG. 2, the valve shaft 10 is connected to a gear 80,
It is driven by motor 70 via 90. Valve stem 10
A return spring 91 is attached to the right end of the throttle valve, and this return spring 91 urges the valve shaft 10 to close the throttle valve in an emergency.

When the valve body made up of the first blade 20 and the second blade 30 is orthogonal to the flow path 40 to block it, the valve is in a closed state, and the valve body rotates clockwise in the figure. As it rotates, the valve will open. The basic structure of such a valve as a whole is the same as that of a conventionally used rotary plate valve such as a butterfly valve.

In this embodiment, by improving the cross-sectional shapes of the first blade 20 and the second blade 30, the load torque applied from the flow during rotation is reduced. Each side portion 20, 30 of the plate-shaped valve body is formed into a convex shape curved in a sinusoidal curve toward the direction of rotation when opening, and the entire plate-shaped valve body is approximately in an inverted S-shape. is doing.

Now, in order to understand in detail the mechanism of the low torque which is an effect of the present invention, computational fluid analysis was performed in comparison with a conventional throttle valve.

In order to perform numerical analysis, the object is modeled as a flow around a valve placed between two-dimensional parallel walls. The assumptions for the analysis conditions assuming an automobile air intake throttle valve are as follows.

(2) Considering the compressibility of the working fluid (air), assume irreversible change. ■As a boundary condition, the fluid on the upstream inlet side of the channel remains stagnant, and the pressure P∞ = 1.013 × 10-6 dyn/cm2 (1a
tm), density ρ∞=1.225×10−3 g/cm3.

■Q=2500 from the downstream side of the flow path

0039
]

[Outside 1]

It is assumed that a fluid of /min is being forcibly drawn in. ■Full length of flow path

[0041]

[Outside 2]

=200mm, from the upstream inlet end face

[
0043

[Outer 3]

It is assumed that the throttle valve is located at 1=50 mm. The results of numerical analysis under the above conditions will be explained below.

(1) Comparison of load torque characteristics FIG. 4 shows the results obtained from the analysis of the static pressure around the valve for the rotary plate valve of the present invention equipped with the first and second vanes 20 and 30 described above. The relationship between the load torque T and the opening degree φ of the valve (denoted as Invention 1) is shown. In the present invention 1, the thickness a of the convex shape is
= 1/4L. In the same figure, the same conditions (above
The results of the conventional throttle valve (conventional example) analyzed in ~■) are shown together with the actual measured values (symbol ○).

In the conventional valve (dashed line), the load torque is T>0 over the entire range of throttle opening, and the load torque has a peak value of T=160 gcm near the opening φ=35°. In the present invention (solid line), when φ<45°, T<0 (valve opening direction), and the maximum negative value of torque is Tmax=-20 gcm.

■When φ>45°, T>0, and the maximum positive value of torque is Tmax=10 gcm.

Therefore, it can be seen that in the throttle valve of the present invention, the absolute value of torque is reduced to 1/8 of that of the conventional valve, and the rate of change of torque with respect to opening can be significantly reduced.

(2) Comparison of Flow Velocity Vectors In order to understand the torque reduction mechanism of the present invention in more detail, the analysis results will be discussed by comparing the conventional valve and the present invention.

■ FIG. 5 shows the speed vector (a) and pressure distribution (b) of the conventional valve at the opening degree φ=50°. First, if we pay attention to the flow on the upstream side of the first blade {corresponding to 101 in Figure 1(B)}, the flow on the wall surface toward the first opening (104 in the same figure) is smooth due to the flow path. Therefore, the velocity vector is large. On the other hand, the second opening (105 in the same figure)
Regarding the flow toward the wall, there is almost no flow along the wall surface, and the velocity vector is extremely small.

■ FIG. 6 also shows the velocity vector (a) and pressure distribution (b) of the present invention at φ=50°. In the flow on the upstream side of the first blade {corresponding to 201 in Figure 1(A)}, the flow velocity vector on the wall toward the first opening (204 in the same figure) is clearly Smaller than conventional valves. On the other hand, if we pay attention to the flow on the wall toward the second opening (205 in the figure), the flow velocity vector is sufficiently large compared to the conventional valve.

From the above results, it can be seen that in the throttle valve of the present invention, the dynamic pressure on the first upstream wing surface is smaller (on the contrary, the static pressure is larger) and the dynamic pressure on the second upstream wing surface is smaller than in the conventional valve. It can be seen that the dynamic pressure becomes large (the static pressure becomes small). As a result, the load torque can be reduced. In addition, as can be seen from the flow velocity vector diagrams {Figures 5 (a) and 6 (a)}, the magnitude of the flow velocity vector varies greatly depending on the location on the upstream wing surface, whereas it varies greatly on the downstream wing surface. The difference in size is small. Therefore, it can be seen that the main factor determining torque largely depends on the shape of the upstream blade.

Furthermore, from the results of numerical calculations, if we compare the flow rates flowing into the first opening and the second opening when the opening degree is φ=50°, we find that (Table 1) Ta.

[0054]

[Table 1]

As is clear from the results shown in Table 1, in the conventional valve, there is a bias in the amount of flow flowing into the first opening and the second opening, making it difficult to maintain a smooth flow path. It can be seen that although the flow rate flowing into the first opening is large, the magnitude of the flow rate is reversed in the present invention in which the throttle shape is improved.

(3) Comparison of pressure distribution FIG. 7 shows the results of comparing the pressure difference on the blade surface between the valve of the present invention and the conventional valve. As shown in FIG. 3, the x coordinate is taken along the blade surface, the valve axis is set as x=0, and the direction toward the first opening 50 is set as x>0. The vertical axis of the graph is the pressure difference ΔP between the upstream and downstream sides of the blade, and the horizontal axis is x/x, where L is the length of one side of the blade.
It is made dimensionless by L.

In the conventional valve (dashed line), the pressure difference ΔP is minimum at the first blade tip and maximum at the second blade tip, causing a large imbalance in pressure distribution around the valve shaft. I can see that

In the throttle valve according to the embodiment of the present invention, the maximum value of ΔP is between the valve shaft (x=0) and the first blade tip (first blade surface), and the maximum value of ΔP is between the valve shaft (x=0) and the first blade tip (first blade surface). The pressure has a minimum value between the blade tips (second blade surface). This is because, as explained in the "effects of the present invention", the first blade is a "flow along an obtuse angle",
Therefore, the pressure is maximum, and the second wing is a ``flow around an acute angle'', which supports the intuitive guess that the pressure is minimum.

Note that the throttle valve according to the embodiment of the present invention is as follows:
Although it has an inverted S-shape, this depends on the viewing direction; for example, if you look at the valve from the back side of the drawing in FIG. 3, the valve will have an S-shape.

Other embodiments of the present invention will be described below. FIG. 4 shows the analysis results of the load torque characteristics in the case where the ratio of the length L to the thickness a of one side of the blade is a=1/8L according to the present invention 2 (indicated by a dashed line). Also in this case, the load torque T is smaller than in the conventional example. However, in the second aspect of the invention, as the opening degree φ of the valve increases, the load torque T tends to increase, so it is preferable to use the valve opening in a relatively small range.

[0061] The first blade 20 and the second blade 30 may have shapes other than those in the embodiments described above.

For example, it is preferable that the convex shape of each side portion of the plate-shaped valve body changes smoothly along the fluid flow. Specifically, as in the example shown in FIG. Smooth curved shapes such as sinusoidal or arcuate shapes are suitable, but as shown in Figure 8, each wing has a
It may be recessed in a curved straight line, such as a ``H'' shape.

Alternatively, as shown in FIGS. 9 and 10, irregularities may be formed only in a part of the plate-shaped valve body.

[0064] Both side portions 20 and 30 of the first and second wings are
Although it may be rotationally symmetrical with respect to the valve shaft 10 as in each of the embodiments described above, it is also possible to change the concave shape, curvature, etc. of the both side portions 20 and 30. Both sides part 2
By making the shapes of 0 and 30 asymmetric, it is possible to adjust how the load torque T is applied (not shown).

Of the both side portions 20 and 30 of the plate-shaped portion, only one side may be formed into a convex shape in the direction in which the plate-shaped valve body rotates and advances when the valve is opened. That is, as shown in FIG. 11, it is possible to make only one side portion 20 of the plate-shaped valve body convex, and leave the opposite side portion 30 flat. Furthermore, in the embodiment shown in FIG.
One side opposite to that shown in FIG. 11 has a convex shape, and the opposite side 30 is flat.

Furthermore, the load torque can be further reduced by changing the shape of the flow path 40 as well as the shape of the plate-shaped valve bodies 20, 30 to change the flow of fluid near the plate-shaped valve bodies 20, 30. (not shown).

[0067] Furthermore, the shape of the blades, for example, as shown in FIG. 3, is as follows: (1) They are bent only in the direction of the flow path, and are not bent in the direction perpendicular to the drawing.

(2) It is bent in the direction of the flow path, and even in the vertical direction of the drawing, it is bent so as to have a bottom at the center, just like the shape of a spoon.

The effects of the present invention can be obtained in both (1) and (2) above. The above (2) will be explained in more detail.

FIG. 13 shows an example of this, in which the valve is not only oriented in the flow direction (white arrow in FIG. 13) but also in the valve shaft 3.
00 (direction perpendicular to the drawing). This allows the flow passing through the sides of the blades 301 and 302 (E in the figure) to be changed from the flow in the case of a conventional valve (Fig. 1
This is to reduce it to the same level as E') in (b). When the shape of the flow path 303 is circular, the opening between the valve and the flow path (the passage connecting the upstream side and the downstream side) is located at the blade tip 30.
4,305 as well as on the sides of the wing, from which the fluid flows out like stream E.

[0071] By making the blade shape curved in the valve axis direction, it is possible to reduce as much as possible the flow E from the side that passes directly without following the unevenness of the blade, and the present invention can be utilized more effectively. , it is possible to achieve low torque of the valve. Since the valve shape of the present invention is difficult to understand intuitively,
Figure 1 shows an arrow view of the valve drawn using computer graphics.
Shown in 4 (a). Figure 15 (b) shows the valve viewed from the Z direction, and Figures 15 (a) and (b) are B-B in Figure 14 (a), respectively.
and a sectional view taken along line CC.

FIG. 16A shows an embodiment of a throttle valve in which a flat portion 404 is provided at the center of the valve (bolt attachment portion) to facilitate attachment of the valve shaft 400 and the valve. 400 is a valve shaft, 401 is a first blade, 402 is a second blade, and 403 is a flow path. 407 in Figure 17 is a bolt 40 formed on the wing
This is the mounting hole number 5. The actual measurement results of the load torque characteristics of this example are shown in Fig. 4 (symbol

[0073]

[Outer 4]

). In the example shown in FIG. 13 described above, as can be seen by comparing FIGS. 15(a) and 15(b), the inclination (α) of the wing at the origin (at the bolt attachment part) in the same figure varies depending on the position of the X axis. . Therefore, in order to attach the blades 301 and 302 to the valve shaft 300, the shape of the valve shaft 300 must be formed to match the curved surface of the center of the blade, or the blades and the valve shaft 300 must be formed at the same time, for example, by precision casting. Needs to be shaped. However, in the embodiment shown in FIG. 16, even if the blades are formed by press working or the like, which is highly suitable for mass production, the blades can be easily attached to the flat portion formed on the valve shaft 400 with bolts. The first blade 401 and the second blade 402 may have shapes other than those in the embodiments described above. As shown in FIG. 20, each wing may be recessed in a curved straight line shape such as an "H" shape.

Alternatively, as shown in FIG. 21, only a portion of the plate-shaped valve body may be provided with an uneven pattern. Or Figure 22,
As shown in FIG. 23, a first wing 401, a second wing 402
It may be a shape in which either a convex surface or a concave surface is formed.

FIG. 24 shows an example in which a small, low-torque throttle valve according to the present invention is further provided by utilizing the flat part of the blade at the center of the valve shaft in order to adjust the flow rate with high precision when the flow rate is minute.

500 is a blade of a small throttle valve, and 501 is a valve shaft for the small valve. By forming the valve shaft into a double structure, the blades 401 and 402 of the large valve and the blades 500 of the small valve can be independently controlled. The opening degree of the large valve blades 401 and 402 is 0.
In this case, by opening and closing only the blades of the small valve as shown in FIG. 24(a), the valve shaft 501 for the small valve can be adjusted to a sufficiently large opening degree, so that the flow rate can be controlled with high precision. When a large flow rate is required, the small valve is closed and the blades 401 and 402 of the large valve are opened as shown in FIG. 24(b). Figure 25 is Figure 24
The purpose is the same as in the case of , but the throttle opening φ is φ=
This is an example in which a minute flow rate can be adjusted with high accuracy by reducing the rate of change of the flow rate Q with respect to the opening degree φ in the vicinity of 0. End portion 450 of first wing 401 and second wing 4
The end portions 451 of 02 are formed into a blade shape by protruding toward the upstream side and the downstream side, respectively. If we define φ=0 when the flat part 405 of the blade is perpendicular to the flow path direction, then φ=0 and the flow rate Q=0, and the valve is as shown in FIG. 25(a).
It becomes closed like this. Furthermore, even if the valve shaft 400 is rotated by a small angle Δφ as shown in FIG.
1, the flow rate can be made sufficiently small. FIG. 25(C) shows a case where the opening degree φ is sufficiently large. The flow characteristics in the small opening range of the present invention shown in FIG. 26 can be arbitrarily selected depending on the shape of the blade tips 450, 451. Of course, the present invention also has the effect of reducing torque.

The rotary plate type valve according to the present invention can be used in various applications such as the above-mentioned intake air throttle valve for automobile engines, butterfly valves for flow rate control in air conditioning plants, chemical plants, etc., vacuum pressure control valves for vacuum equipment, etc. It can be applied to rotating plate valves used in the technical field.

[0079]

Effects of the Invention As described above, the rotary plate valve according to the present invention significantly reduces the load torque when rotating the valve by improving the shape of the plate-shaped valve body attached to the valve stem. can be reduced to

Specifically, the valve includes a first blade that moves downstream when opening in the flow direction, a second blade that moves upstream in the flow direction, and the first and second blades. body and
It is composed of a valve shaft that supports the valve body, a flow path that rotatably accommodates the valve body via the valve shaft, and that guides the fluid, and (1) the first blade is arranged in the flow direction. On the other hand, it has a concave shape that receives fluid.

(2) The second blade has a convex surface in the flow direction and has a shape that receives the fluid. By configuring the structure to satisfy one or both of the above conditions, it is possible to reduce the imbalance in the static pressure applied to both sides of the plate-shaped valve body,
The load torque caused by this static pressure imbalance can be reduced.

[0082] By reducing the load torque required for rotating the valve, control stability is improved and it becomes possible to finely adjust the engine output.

Further, according to the present invention, the diameter of the throttle valve can be made larger than before. Generally, it is preferable to reduce as much as possible the ratio of the throttle valve that acts as a resistance to the intake air amount of the engine during maximum output operation of the engine, and therefore it is desirable to make the diameter relatively large. In conventional throttle valves, the load torque increases in proportion to the cube of the diameter, and therefore there is a limit to increasing the inner diameter of the flow path.However, by adopting the valve shape of the present invention, the load torque increases in proportion to the cube of the diameter. A control system can be configured with actuators.

Since butterfly valves are used as fluid control equipment in various fields, the present invention can greatly contribute to electronic control of flow rate regulation, and its effects are tremendous.

[Brief explanation of the drawing]

[Figure 1] (a) Model diagram of the present invention (b) Model diagram of conventional example

[Fig. 2] Cross-sectional view showing an embodiment of the present invention

[Figure 3] A-A sectional view in Figure 2

[Figure 4] Graph showing load torque curve

[Figure 5] (a) Flow velocity vector diagram of conventional valve (b) Pressure distribution diagram of conventional valve

[Figure 6] (a) Flow velocity vector diagram of the present invention (b) Pressure distribution diagram of the present invention

[Figure 7] Graph showing pressure distribution on the wing surface

FIG. 8 is a sectional view showing another embodiment of the present invention.

FIG. 9 is a sectional view showing another embodiment of the present invention.

FIG. 10 is a sectional view showing another embodiment of the present invention.

FIG. 11 is a sectional view showing another embodiment of the present invention.

[Figure 12
]Cross-sectional view showing another embodiment of the present invention

FIG. 13 is a sectional view showing another embodiment of the present invention.

[Fig. 14] (a) Computer graphics of the valve of the embodiment shown in Fig. 13; (b) Computer graphics of the valve of the embodiment of Fig. 13;

[Figure 15] (a) BB cross-sectional view in Figure 14 (a) (b) CC cross-sectional view in Figure 14 (a)

FIG. 16 is a sectional view of another embodiment of the present invention.

[Figure 17] (A) Front view of Figure 16 (B) BB sectional view of Figure 17 (A) (C) CC sectional view of Figure 17 (A)

[Figure 18] (a) Computer graphics of the wing (b) Computer graphics of the wing (c) Computer graphics of the wing

[Figure 19] (A) B of Figure 18 (A)
-B sectional view (B) C-C sectional view in Figure 18 (A)

FIG. 20 is a sectional view showing another embodiment of the present invention.

[Figure 21]
A sectional view showing another embodiment of the present invention

FIG. 22 is a sectional view showing another embodiment of the present invention.

FIG. 23 is a sectional view showing another embodiment of the present invention.

[Fig. 24] (A) Cross-sectional view showing another embodiment of the present invention (B) Cross-sectional view of the same

[Fig. 25] (A) Cross-sectional view showing another embodiment of the present invention (B) Cross-sectional view (C) Cross-sectional view

[Figure 26] Diagram showing the relationship between flow rate and throttle opening

[Figure 2
7] Cross-sectional view of conventional example

Claims (7)

[Claims] 1. A valve including a first blade that moves downstream when opening in the flow direction, a second blade that moves upstream in the flow direction, and the first blade and the second blade. The valve body is composed of a valve body, a valve shaft that supports the valve body, and a flow path that rotatably houses the valve body via the valve shaft and guides fluid, and the first vane is arranged in a direction opposite to the flow direction. A rotary plate type valve characterized in that the second vane is formed to have a concave shape to receive fluid, or the second vane is formed to have a convex surface to receive fluid in the flow direction. 2. A valve including a first blade that moves downstream when opening in the flow direction, a second blade that moves upstream in the flow direction, and the first blade and the second blade. The valve body is composed of a valve body, a valve shaft that supports the valve body, and a flow path that rotatably accommodates the valve body via the valve shaft and guides fluid, and the first vane is arranged such that the first vane is oriented in the flow direction. 1. A rotary plate valve characterized in that the second vane is formed to have a concave shape to receive fluid, and the second blade has a convex shape to receive fluid in the flow direction. 3. A valve including a first blade that moves downstream when opening in the flow direction, a second blade that moves upstream in the flow direction, and the first blade and the second blade. the valve body, a valve shaft that supports the valve body, and a flow path that rotatably accommodates the valve body via the valve shaft and guides fluid, and the first blade is configured to control the flow direction and the valve body. The second blade is formed to have a concave surface in the axial direction to receive the fluid, or the second blade is formed to have a convex surface in the flow direction and the valve axis direction to receive the fluid. Rotating plate type valve. 4. A valve including a first blade that moves downstream when opening in the flow direction, a second blade that moves upstream in the flow direction, and the first blade and the second blade. the valve body, a valve shaft that supports the valve body, and a flow path that rotatably accommodates the valve body via the valve shaft and guides fluid, and the first blade is configured to control the flow direction and the valve body. The second blade is formed to have a concave shape in the axial direction to receive the fluid, and the second blade is formed to have a convex shape in the flow direction and the valve axis direction to receive the fluid. Features a rotating plate valve. 5. The concave surface of the first wing or the convex surface of the second wing is formed by a curved surface such as a circular arc or a sine curve. Rotating plate valve as described. 6. The concave surface of the first blade or the convex surface of the second blade has curved surfaces protruding from the upstream side and the downstream side, respectively, when the valve is closed and the flow rate is approximately zero. Claims 1 to 4 are characterized in that:
A rotary plate valve according to any of the above. 7. The rotary plate valve according to claim 2, wherein the valve body has a generally S-shaped cross section.