JP2001012825A - Throttle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a throttle device with a large throttle amount and a low noise level. SOLUTION: In the throttle device where a valve rod 1 provided in a valve chamber 8 communicating with inlet piping 10 is brought into contact with or separated from a valve seat 2 of a valve port 9 interposed between the valve chamber 8 and outlet piping 11, a first throttling part is formed between the valve seat 2 and a step surface 12c of the valve rod 1 in contact with the valve seat 2 by a cutting groove 3 that is formed on a step surface 12c between a large-diameter part 12a and a small-diameter part 12b of the valve rod 1, at the same time a second throttling part communicating with the first throttling part is formed between a tip surface 12d of the valve rod 1 where the step surface 12c is in contact with the valve seat 2 and the step surface of a large- diameter part 6a and a small-diameter part 6b of the valve port 9, thus forming a throttling passage where fluid that is directed from a valve chamber 8 to the outlet piping 11 is throttled in steps while the valve seat and the step surface of the valve rod 1 is in contact to each other in the first and second throttling parts.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a throttle device provided in a fluid circuit through which a fluid passes.

[0002]

2. Description of the Related Art For example, in a throttling device provided in a refrigeration cycle of an air conditioner, noise may be generated due to the flow of the refrigerant, and various means for reducing the flow noise of the refrigerant have conventionally been proposed. Have been.

As one example, Japanese Patent Application Laid-Open No. 7-248162
In the solenoid valve described in Japanese Patent Application Laid-Open Publication No. H11-115, when a solenoid rod is energized and stopped, a valve rod that reciprocates in the axial direction together with the plunger is provided with a through hole passing through the axis thereof, and when this solenoid valve is used as a throttle, By energizing the solenoid coil to move the valve stem, the valve is closed by a valve element formed at one end of the valve stem, and the opening of the secondary pipe is closed.

Then, in a state where the valve element is closed, the valve extends from the primary side pipe to the other end of the valve rod through a gap outside the plunger, and further passes through a flow hole from the one end of the valve rod to the secondary side. By forming a leakage passage leading to the side pipe, the refrigerant passing through the leakage passage is decompressed a plurality of times in the leakage passage, thereby reducing the refrigerant passage noise when using the solenoid valve as a throttle. I have.

Another conventional example is disclosed in Japanese Patent Laid-Open No. 8-93.
In the electric flow control valve described in Japanese Patent No. 945, a valve body is connected to a valve holder screwed into a cylindrical bush, and the valve body is moved in a circumferential direction with respect to the cylindrical bush by operating a stepping motor. By reciprocating in the axial direction while rotating, that is, by spiraling, the valve is opened and closed by the valve body, and when the valve is closed by the valve body, the opening of the secondary side pipe is configured to be closed. I have.

When a gas-liquid mixed refrigerant in which a gas refrigerant and a liquid refrigerant are mixed flows into the electric flow control valve from the primary side pipe, the valve is brought into a state immediately before the valve is completely closed by a valve body.
The liquid refrigerant is caused to flow from the primary pipe to the secondary pipe through a valve constriction portion, which is a slight gap between the valve seat of the valve and the valve body, and the gas refrigerant is communicated with the primary pipe. By flowing the gas refrigerant from the primary pipe to the secondary pipe through an internal passage formed from the valve element to the valve holder, and preventing the gas refrigerant from passing through the valve constriction, generation of bubble gas and Noise is prevented from being generated due to the rupture.

As another conventional example, Japanese Patent Application Laid-Open No. 5-28
In the expansion valve described in Japanese Patent No. 8286, a fixed feed screw is screw-coupled to a valve stem connected to a stator of a stepping motor, and the valve stem is rotated in the circumferential direction with respect to the feed screw by the operation of the stepping motor. Reciprocating in the direction, that is, by helical operation, the valve is opened and closed by the valve element at the tip of the valve rod, and when the valve is closed by the valve element, the opening of the secondary side pipe is configured to be closed. I have.

[0008] A plurality of grooves extending in the axial direction of the valve stem are formed on the peripheral surface of the valve element portion of the valve stem at locations spaced apart in the circumferential direction of the valve stem. In the valve body portion of the valve stem, an internal passage communicating the valve stem tip and the peripheral surface of the valve body portion is formed, and in a state where the valve is closed by the valve body, the gap between the inner peripheral wall of the valve seat and the groove, Alternatively, the gap and the internal passage of the valve stem secure a plurality of flow paths for communicating the primary pipe and the secondary pipe at a low flow rate.

Thus, in the expansion valve described in Japanese Patent Application Laid-Open No. 5-288286, especially when the refrigerant is a gas-liquid mixed refrigerant in which a gas refrigerant and a liquid refrigerant are mixed, the flow path of the gas refrigerant and the liquid refrigerant Can be secured separately, thereby making it possible to prevent generation of noise due to generation and rupture of bubble gas and generation of blockage of a throttle by a bubble mass.

Further, as another conventional example, Japanese Utility Model Application Laid-Open No.
In the expansion valve described in JP-A-54164, the valve connected to the opening of the secondary pipe is opened and closed by a valve body constituted by a plunger by energizing and stopping the solenoid coil, and a valve seat of the valve is provided with a valve seat. 1 from the opening of the secondary pipe
A groove reaching the opening of the secondary pipe is formed, and in a state where the valve is closed by the valve body, the refrigerant flowing from the primary pipe to the secondary pipe is restricted by the groove of the valve seat. I have.

[0011]

However, first, a solenoid valve described in JP-A-7-248162 and a solenoid valve disclosed in JP-A-8-248162 are disclosed.
The motor-operated flow control valve described in JP-93945 has the following problems.

That is, in order to obtain a large throttle amount in configuring the throttle valve, it is sufficient to increase the fluid resistance of the throttle portion. If this is applied to the solenoid valve described in Japanese Patent Application Laid-Open No. 7-248162, Either the cross-sectional area of the leak passage is reduced or the length of the leak passage is lengthened.
If applied to the electric flow control valve described in 3945,
The cross-sectional areas of the throttle passage for the liquid refrigerant formed by the slight gap between the valve body and the valve seat and the internal passage for bypassing the gas refrigerant are reduced.

However, the leakage path of the solenoid valve described in Japanese Patent Application Laid-Open No. 7-248162,
Regardless of the throttle passage or the internal passage of the electric flow control valve described in JP-A-5, the cross-sectional area of the passage is considerably smaller than that of the primary pipe or the secondary pipe.

For this reason, if these passages having originally small cross-sectional areas are further reduced in cross-sectional area, adhesion and accumulation of dust and the like existing in the refrigerant circulating in the refrigeration cycle, and formation of the passages due to the adhesion and accumulation of dust and the like will occur. Blockage is likely to occur, resulting in adverse effects such as impaired throttling function and poor circulation of the refrigerant in the refrigeration cycle.In addition, whistling noise and fluctuation noise are generated by minimizing the passage diameter. In addition, the flow rate of the refrigerant may increase and the noise level of the continuous flow noise may increase, so that such a configuration cannot be easily adopted.

In addition, the above-mentioned Japanese Patent Application Laid-Open No. 7-248162
In a valve for restricting a gas-liquid mixed refrigerant, such as an electromagnetic valve described in Japanese Patent Application Laid-Open Publication No. H8-209 and an electric flow control valve described in Japanese Patent Application Laid-Open No. Hei 8-93945, a gas that is a compressible fluid and a non-compressible fluid Since a certain liquid alternately passes through a narrow passage for throttling with different flow resistances, flow fluctuations and pressure fluctuations occur in the refrigerant and act as a vibrating force on the valve, resulting in discontinuous flow noise. However, if the cross-sectional area of the throttling passage is reduced, there is a possibility that the noise level of the discontinuous flow noise generated in the above-described process may be increased.

If the gas-liquid mixed refrigerant is a slug flow or a plug flow in which shell-shaped bubbles and liquid alternately appear, the flow noise is intermittent and the noise level is originally very large. In a throttle valve that throttles a gas-liquid mixed refrigerant of such a slag flow or a plug flow, when the cross-sectional area of the throttle passage is reduced as described above, the degree of increase in the noise level of the discontinuous flow noise is not half-life. It will not stop.

Next, the expansion valve described in JP-A-5-288286 has the following problems.

That is, in this expansion valve, since a plurality of grooves extending in the axial direction of the valve stem are formed at intervals in the circumferential direction of the valve stem, the electromagnetic valve described in JP-A-7-248162 is disclosed. The noise problem described above is somewhat alleviated as compared with a valve and a structure having a single throttle passage, such as an electric flow control valve described in JP-A-8-93945.

However, with respect to the problem of adhesion and accumulation of dust and the like present in the refrigerant circulating in the refrigeration cycle and the obstruction of the passage due to the adhesion and accumulation of dust and the like, each groove of the valve stem and the inner peripheral wall of the valve seat are not covered. If the cross-sectional area of the flow path constituted by the gap becomes small, there is a possibility that the flow path may naturally occur in each flow path, and the fundamental solution cannot be achieved.

In addition, the movement of the valve body or the valve stem with respect to the valve seat at the time of opening the valve is a helical operation that combines rotation around the axis of the valve stem and axial movement of the valve stem. Since any of the axial movements is not a movement in the direction of increasing the gap between each groove of the valve stem and the inner peripheral wall of the valve seat, it is constituted by the gap between each groove of the valve stem and the inner peripheral wall of the valve seat. If the cross-sectional area of each flow path is too small, dust and the like present in the refrigerant circulating in the refrigeration cycle will be clogged in each flow path, and the valve stem will not move with respect to the valve seat when the valve is opened, causing a lock. there's a possibility that.

The lock of the valve stem is disclosed in Japanese Patent Laid-Open No. 5-2882.
As described in Japanese Patent Publication No. 86, the bottom surface of the groove of the valve stem may be parallel to the inner peripheral wall of the valve seat, or may be tapered inclined with respect to the inner peripheral wall of the valve seat. there's a possibility that.

In the expansion valve described in Japanese Patent Application Laid-Open No. 5-288286, as described above, the movement of the valve body or the valve stem with respect to the valve seat at the time of opening is a spiral operation. The relative position of each flow path formed by the gap between each groove of the valve stem and the inner peripheral wall of the valve seat with respect to the valve seat constantly changes in the rotation direction of the valve stem. A change in the relative position causes a subtle change in the flow rate of the refrigerant passing through each flow path.

Therefore, the change in the flow rate of the refrigerant in each flow path changes the balance of the fluid force exerted by the refrigerant on the valve stem, causing the valve stem to vibrate. The size and size are not constant, resulting in noise that can be heard.

Next, the expansion valve described in Japanese Utility Model Laid-Open Publication No. 61-54164 has the following problems.

That is, also in this expansion valve, since the refrigerant is throttled by the groove of the valve seat, if the cross-sectional area of this groove is made too small in order to obtain a large throttle amount, as in the other conventional valves described above, Adhesion and accumulation of dust and the like present in the refrigerant circulating in the refrigeration cycle and blockage of the passageway due to the adhering and debris are likely to occur, resulting in adverse effects such as impairment of the throttling function and poor circulation of the refrigerant in the refrigeration cycle. May occur.

In addition, in the case of this expansion valve, the actual opening
As described in Japanese Patent Application Publication No. 1-54164, the bottom of the groove of the valve seat is one step higher than the opening of the primary pipe,
Refrigerant flowing from the primary pipe through the valve into the secondary pipe may pass through a location considerably higher than the groove of the valve seat when crossing the level difference between the two, and therefore, when the valve is opened. It is hardly expected to remove the dust and the like adhering to the groove due to the flow of the refrigerant, and there is a possibility that the dust and the like continue to accumulate in the groove and fill the groove.

In addition, since the expansion valve has a single groove, the above-described problem of the noise level of the flow noise of the refrigerant may occur quite significantly.

In addition, in this expansion valve, a single groove extends in the radial direction of the valve rod, and the refrigerant that flows into the groove from the primary side pipe and is throttled by passing through this groove closes the valve. By colliding with the peripheral surface of the valve stem in the state, the flow direction is changed toward the secondary pipe extending in the axial direction of the valve shaft, so that when the flow direction changes, the refrigerant flow is greatly disturbed. Is generated, and vibration is applied from a direction deviated to the valve stem when colliding with the peripheral surface of the valve stem. As a result, these factors cause the noise level of the flow noise of the refrigerant to further increase. There is fear.

Incidentally, the above-mentioned problem of blockage of the passage, flow path and groove in each conventional valve is not caused solely by dust or the like present in the refrigerant circulating in the refrigeration cycle. When an HFC-based refrigerant is used, there is a possibility that contamination (dirt) or the like in the refrigerant is caused by adhesion and deposition.

The present invention has been made in view of the above circumstances,
An object of the present invention is to provide a diaphragm device having a large diaphragm amount and a low noise level.

[0031]

According to a first aspect of the present invention, there is provided a throttle device according to the present invention, wherein a valve stem provided in a valve chamber communicating with a first passage is provided between the valve chamber and a second valve chamber. In a throttle device that comes into contact with and separates from a valve seat of a valve port interposed between the valve seat and the valve seat, a groove formed in one of the valve stem and the valve seat allows the valve seat and the valve seat to be separated from each other. A first gap is formed between the valve stem and the contacted valve stem, and a second gap communicating with the first gap is formed between the valve stem and the valve port contacted with the valve seat. Then, the first gap and the second gap allow the second space to be removed from the valve chamber.
The fluid flowing toward the passage is formed in a throttle passage that is gradually reduced in a state where the valve seat and the valve stem are in contact with each other.

Further, in the throttle device according to the present invention, the valve stem is provided with a large-diameter portion and a small-diameter portion located on the distal end side of the valve stem with respect to the large-diameter portion. The valve stem is formed such that a step end surface of the small diameter portion and the large diameter portion comes into contact with the valve seat, and the groove is formed in one of the step end surface and the valve seat, The first gap is formed between the end face of the step portion and the valve seat.

Further, in the throttle device according to the present invention, the valve port may include a large-diameter port portion, and the large-diameter port located closer to the second passage than the large-diameter port portion. A small-diameter port portion connected to the portion is provided, and in a state where the end surface of the step portion and the valve seat are in contact with each other, the tip surface of the small-diameter portion is provided at the end surface of the step port portion between the large-diameter port portion and the small-diameter port portion. The valve port is formed so as to face at an interval, and the second gap is formed between the end surface of the stepped port portion and the end surface of the small diameter portion.

According to a fourth aspect of the present invention, the second gap is formed between the outer peripheral surface of the small diameter portion and the inner peripheral surface of the valve port.

Further, in the throttle device according to the present invention, the valve seat portion of the valve seat located at the opening edge of the valve port is located on the outer peripheral surface of the valve stem near the tip of the valve stem. The valve stem and the valve seat are formed so that the outer peripheral surface portions thereof come into contact with each other, and the groove is formed in one of the valve seat portion and the outer peripheral surface portion, so that the valve seat portion and the outer peripheral surface are formed. The first gap is formed between the first gap and the surface portion.

In the throttling device according to the present invention, the valve port may include a large-diameter port portion and the large-diameter port located closer to the second passage than the large-diameter port portion. A small-diameter port portion connected to the portion, and in a state where the valve seat portion and the outer peripheral surface portion are in contact with each other, a tip end surface of the valve stem is provided at an end surface of a stepped port portion between the large-diameter port portion and the small-diameter port portion. The valve port is formed so as to face at an interval, and the second gap is formed between the end face of the stepped port portion and the tip face of the valve stem.

The throttling device according to the present invention as set forth in claim 7, wherein the valve port has a large-diameter port, and the large-diameter port is located on the second passage side of the large-diameter port. A small-diameter port portion connected to the portion, and in a state where the valve seat portion and the outer peripheral surface portion are in contact with each other, the outer peripheral surface portion further contacts a step port portion between the large-diameter port portion and the small-diameter port portion. And the second port formed in one of the step port portion and the outer peripheral surface portion, the valve port is formed between the step port portion and the outer peripheral surface portion. A second gap was formed.

According to the throttle device of the present invention, as the valve stem comes into contact with the valve seat, the valve stem is formed by the groove formed in one of the valve stem and the valve seat. A first gap formed between the valve chamber and the valve seat, and a second gap formed between the valve stem and the valve port and communicating with the first gap, from the valve chamber to the second passage. Since the throttle passage that throttles the fluid that flows in a stepwise manner is formed continuously between the valve chamber and the second passage, the fluid is throttled stepwise by each of the first and second gaps. It is possible to obtain a larger throttle amount in the entire throttle passage.

Further, according to the throttle device of the present invention, the throttle amount in each of the first and second gaps can be smaller than the throttle amount in the entire throttle passage. Accordingly, it is possible to prevent the occurrence and increase of the whistling sound due to the rapid fluctuation of the flow, and the occurrence and increase of the vibration sound due to the application of a large load to the flow of the fluid.

In addition, according to the throttling device of the present invention, when the valve stem is separated from the valve seat, the first gap and the second gap both increase accordingly.
Even if dust and contaminants (dirt) floating in the fluid adhere to and accumulate in each of the second gaps, there is no possibility of locking the valve-opening operation or blocking of the fluid passage. Since the throttle passage is constituted by the first and second gaps, the noise level of the flow noise of the fluid may increase due to the biased flow of the fluid acting on the valve stem. Therefore, even if the cross-sectional area of the throttle passage is reduced to increase the throttle amount, it is possible to prevent inconvenience in operation and noise reduction.

Further, according to the throttle device of the present invention, the groove formed in one of the valve stem and the valve seat is provided between the valve stem and the valve seat. Therefore, by appropriately adjusting the number and the cross-sectional area of the grooves, it is possible to arbitrarily set the throttle amount in the first gap or the entire throttle passage.

According to the throttling device of the present invention, when the end face of the step portion between the large diameter portion and the small diameter portion provided on the valve stem comes into contact with the valve seat, the end face of the step portion and the valve seat are provided. The first gap is formed between the valve seat and the end face of the step portion of the valve stem in contact with the valve seat by the groove formed in any one of the valve seat and the valve seat. Grooves necessary for forming the first gap can be easily formed by simple processing such as cutting of the end face of the step portion of the valve stem or the valve seat.

Further, according to the expansion device of the present invention, when the end face of the step portion of the valve stem comes into contact with the valve seat,
Since the second gap is formed between the end face of the stepped portion of the large-diameter port portion and the small-diameter port portion provided in the valve port and the front end face of the small-diameter portion of the valve stem, the valve stem comes into contact with and separates from the valve seat. By appropriately adjusting the size of the small-diameter portion of the valve stem and the size of the large-diameter port portion of the valve port in the direction in which the valve is closed, it is possible to arbitrarily set the throttle amount in the second gap or the entire throttle passage. .

Similarly, according to the throttling device of the present invention, when the end face of the step portion of the valve stem comes into contact with the valve seat,
Since the second gap is formed between the inner peripheral surface of the valve port and the outer peripheral surface of the small diameter portion, by appropriately adjusting the outer diameter of the small diameter portion of the valve rod and the inner diameter of the valve port, the second gap is formed. In addition, it is possible to arbitrarily set the throttle amount in the entire throttle passage.

Further, according to the throttling device of the present invention, when the outer peripheral surface portion near the tip of the valve stem comes into contact with the valve seat portion located at the opening edge of the valve port, the valve seat portion and The valve seat portion located at the opening edge of the valve port by the groove formed on one of the outer peripheral surface portion near the tip of the valve stem, and the outer peripheral surface portion near the tip of the valve stem in contact with the valve seat portion Since a first gap is formed between the valve seat and the valve seat, a groove necessary for forming the first gap between the valve stem and the valve seat is formed in a valve seat portion located at an opening edge of the valve port, or It can be easily formed by simple processing such as cutting of the outer peripheral surface near the tip of the valve stem.

According to the throttling device of the present invention, when the outer peripheral surface near the tip of the valve stem comes into contact with the valve seat located at the opening edge of the valve port, the valve is provided at the valve port. Since the second gap is formed between the stepped port portion end face of the large diameter port portion and the small diameter port portion and the outer peripheral surface portion near the tip of the valve stem, in the direction in which the valve stem contacts and separates from the valve seat, By appropriately adjusting the size of the valve stem and the size of the large-diameter port portion of the valve port, it is possible to arbitrarily set the throttle amount in the second gap or the entire throttle passage.

Further, according to the throttling device of the present invention, the second port formed on one of the step port portion of the valve port and the outer peripheral surface portion near the tip of the valve stem.
Groove forms a second gap between the valve stem and the valve port. By appropriately adjusting the number and the cross-sectional area of the second groove, the second gap or the entire throttle passage can be formed. Can be set arbitrarily.

Further, according to the throttling device of the present invention, when the outer peripheral surface portion near the tip end of the valve stem comes into contact with the valve seat portion located at the opening edge of the valve port, the step port of the valve port is provided. Since the second gap is formed between the portion and the outer peripheral surface portion near the tip of the valve stem, the second gap is formed between the valve stem and the valve port so as to communicate with the first gap. The necessary second groove can be easily formed by a simple process such as cutting of the step port portion of the valve port or the outer peripheral surface portion near the tip of the valve stem.

[0049]

Embodiments of the present invention will be described below with reference to the drawings.

FIGS. 1 and 2 are longitudinal sectional views showing a diaphragm device according to a first embodiment of the present invention, in which 31 is an electromagnetic coil, 32 is a guide, 33 is a plunger, 34 is a cushioning material,
1 is a valve rod, 35 is a spring, 36 is a suction element, 4 is a valve housing, 37 is a cylindrical portion, 3 is a cut groove, 2 is a valve seat, 8 is a valve chamber, 9 is a valve port, 10 and 11 are piping. It is.

In the figure, a valve chamber 8 is provided inside the valve housing 4, and the valve rod 1 is provided in the valve chamber 8.
Are provided movably in the vertical direction on the drawing. The valve chamber 8 is formed with a valve seat 2 having a valve port 9 communicating with an outlet pipe 11 (corresponding to a second passage in the claims). The valve chamber 8 is on the high pressure side and the valve port 9 is on the low pressure side.

The valve port 9 has a large diameter portion 6a on the valve chamber 8 side.
(Corresponding to the large-diameter port portion in the claims) and the large-diameter portion 6a
And a small-diameter portion 6b (corresponding to a small-diameter port portion in the claims) on the outlet pipe 11 side having a smaller inner diameter.

A cylindrical portion 37 is integrated with the valve housing 4 by brazing or the like, and a guide 32 is provided at an upper portion in the drawing, and a suction element 36 is provided at a lower portion in the drawing. Plunger 3 integrated with valve stem 1 in between
3 are arranged. The plunger 33 is formed in a cylindrical shape, and the cylindrical portion is formed between the projecting portion of the guide 32 and the cylindrical portion 37.
And is located between.

The plunger 33 is provided with a suction element 36.
, Ie, the guide 32
Is biased in the direction to approach. Further, the cylindrical portion 37
An electromagnetic coil 31 is provided on the outer surface side of.

A cushioning material 34 is provided on the flange-like end surface of the guide 32 facing the tip of the plunger 33. The guide 32 regulates the movement of the plunger 33 due to the urging force of the spring 35. It is a stopper.

With this configuration, when the electromagnetic coil 31 is energized, the electromagnetic force between the suction element 36 and the plunger 33 in the direction of lowering the plunger 33 on the drawing against the urging force of the spring 35. Occurs.

The distal end of the valve stem 1 is shaped like a bell which sits inside from the tip end side, and the outer peripheral surface of the distal end of the valve stem 1 is larger than the inner diameter of the large diameter portion 6 a of the valve port 9. A large diameter portion 12a having an outer diameter slightly larger than the large diameter portion 12a and disposed closer to the distal end of the valve stem 1 and slightly larger than the inner diameter of the small diameter portion 6b of the valve port 9 and larger than the inner diameter of the large diameter portion 12a. The small diameter portion 12b having a small outer diameter is formed in a step shape.

As shown in the enlarged sectional view of the main part in FIG. 3, a plurality of peripheral surfaces at intervals in the circumferential direction of the valve stem 1 of the peripheral surface at the distal end of the valve stem 1 are provided. Diameter part 12a
A hole 5 is formed by a drill or the like so as to straddle the small diameter portion 12b and the large diameter portion 12a and the small diameter portion 1b.
Step surface 12c with step 2b (corresponding to step end face in claims)
In addition, a plurality of cut grooves 3 having a semicircular cross section (corresponding to grooves in the claims) are provided at intervals in the circumferential direction of the valve stem 1.

In this configuration, when the electromagnetic coil 31 is energized, as shown in FIG. 1, a large electromagnetic force generated between the attraction element 36 and the plunger 33 causes the plunger 33 to resist the urging force of the spring 35. Then, the valve is pushed down until it comes into contact with the suction element 36, and the valve rod 1 is brought into a closed state in which the tip of the valve rod 1 contacts the valve seat 2.

At this time, as shown in FIG. 3, the cut groove 3 provided on the step surface 12c between the large-diameter portion 12a and the small-diameter portion 12b of the valve stem 1, and the large size of the valve port 9 of the valve seat 2. A first throttle portion 13a (corresponding to a first gap in the claims) is formed by the distal end surface portion of the diameter portion 6a, and the small diameter portion 12 of the valve stem 1 is formed.
b, and a stepped surface 6c of the large diameter portion 6a and the small diameter portion 6b of the valve port 9 (corresponding to an end surface of the stepped port portion in the claims) to form a second throttle portion 13b (second in the claims). (Corresponding to a gap).

The outer peripheral surface of the small-diameter portion 12b of the valve stem 1 and the inner peripheral surface of the large-diameter portion 6a of the valve port 9 form the first throttle 1
A connection passage 14 is formed to allow the 3a and the second throttle portion 13b to communicate with each other. A throttle passage is formed by the first throttle portion 13a, the connection passage 14, and the second throttle portion 13b.
Through the throttle passage, the inlet pipe 10 (the first pipe in the claims)
The valve chamber 8 and the outlet pipe 11 communicating with the
Connected in valve closed state.

On the other hand, when the energization of the electromagnetic coil 31 is stopped, the above-mentioned electromagnetic force disappears, so that as shown in FIG.
When the plunger 33 is biased by the spring 35,
4 is pushed up until the tip of the plunger 33 comes into contact with the plunger 33, whereby the valve stem 1 is lifted to be in an open state separated from the valve seat 2.

Therefore, the first throttle portion 13a, the connection passage 1
4 and the second throttle portion 13b are eliminated, and the valve chamber 8 communicates with the outlet pipe 11 via the valve port 9.

In the throttle device according to the first embodiment having such a configuration, if the inner diameter D1 of the small diameter portion 6b of the valve port 9 is at least as large as the inner diameter D2 of the outlet pipe 11,
When the valve stem 1 is fully opened, a loss only occurs due to a pressure drop caused by a change in the direction of the flow of the fluid from the valve chamber 8 to the outlet pipe 11 via the valve port 9. Will be formed.

When the valve stem 1 is fully closed, the first throttle 1
A throttle passage consisting of 3a, connection passage 14 and second throttle 13b is formed, resulting in the required pressure drop.

The inner diameter D1 of the small diameter portion 6b of the valve port 9
Is smaller than the inner diameter D2 of the outlet pipe 11, a throttle effect occurs even when the valve rod 1 is fully opened due to the difference in the inner diameter. Therefore, this throttle device is a throttle valve having a different throttle amount between when fully opened and when fully closed. become.

Further, in the stop device of the first embodiment shown in FIGS. 1 to 3, the first stop portion 13a and the second stop portion 13
b, which has a two-stage aperture ratio,
In order to secure the same amount of aperture, compared to the case of one-step aperture,
The amount of aperture per one aperture may be small. Thereby, the first throttle unit 13a and the second throttle unit 13b, and eventually,
The cross-sectional area of the entire throttle passage can be increased.

Since it is experimentally known that the flow noise increases linearly with the square of the flow velocity, that is, the square of the flow rate, the throttle device having the above-described structure can be used. The flow velocity of the fluid at the outlet can be reduced, and the flow noise can be reduced.

FIG. 6 shows a throttle device in which the throttle passage is constituted by a one-stage throttle for comparison with the throttle device according to the first embodiment. In this throttle device, a cut groove 3 is formed on the valve seat 2 side, not the valve rod 1 side, so as to approach the center side of the outlet pipe 11 from the valve chamber 8 toward the outlet pipe 11. When the valve 1 is fully closed, the constricted portion 13 is formed by the tapered surface 15 formed on the outer peripheral surface of the distal end portion of the valve stem 1 and the cut groove 3.

FIG. 6 having such a one-stage throttle passage
Compared with the throttle device of the first embodiment, in the throttle device of the first embodiment shown in FIGS. 1 to 3, even if the entire throttle amount and the flow rate of the fluid are all the same value, the generated flow noise is as shown in FIG. Is smaller than the aperture device.

FIG. 7 shows the noise level of the flow noise generated in the throttle device when the gas-liquid two-phase flow is passed through the throttle device.
It is a graph which shows the result of having experimentally calculated | required the relationship with the flow velocity of the fluid in the outlet of a throttle apparatus, According to this experimentally determined result, a noise level is linear with respect to the square of the flow velocity of the fluid in an outlet. Because of the variation, reducing the outlet flow velocity of the fluid will reduce the noise level by the square of the flow velocity.

Therefore, even if the same aperture amount is obtained,
It is possible to set a larger cross-sectional area of the diaphragm by dividing the diaphragm into two stages and narrowing the diaphragm than in one stage, and as a result, for example,
If the cross-sectional area of the outlet is doubled, the outlet flow velocity can be suppressed, and the noise level of the fluid can be suppressed, such that the outlet flow velocity can be reduced by 6 dB.

As described above, the flow noise can be further reduced by connecting the throttle portions with a plurality of throttle ratios and reducing the pressure of the fluid in multiple stages.

In the throttle device according to the first embodiment, the inner surface of the cutout groove 3 of the valve rod 1 and the valve housing 4 around the valve seat 2 constituting the first throttle portion 13a communicating with the valve chamber 8. 4, the valve opening operation of the valve stem 1 is performed in a direction to widen the gap between the floating member 53 and the floating material 53 in the pipe.
Even if is adhered and deposited on the first throttle portion 13a, the valve rod 1 is operated to open as shown in FIG. 5, and the inner surface of the cut groove 3 of the valve rod 1 and the valve housing 4 around the valve seat 2. Is separated, the suspended matter 53 is left on the inner surface of the valve housing 4 and flows toward the outlet pipe 11 by the flow of the fluid from the inlet pipe 10 to the outlet pipe 11 via the valve chamber 8.

Further, the valve-opening operation of the valve stem 1 is controlled by the notch groove 3 of the valve stem 1 forming the first throttle portion 13 a communicating with the valve chamber 8 and the inner surface of the valve housing 4 surrounding the valve seat 2. Since the operation is performed in the direction in which the gap is widened, there is no possibility that the floating material (dust, contamination, or the like) enters the first throttle portion 13a and the valve rod 1 does not enter the locked state where the valve cannot be opened.

In addition, in the aperture device according to the first embodiment, the aperture amount per stage can be reduced and the cross-sectional area of the aperture portion can be increased as compared with the case where the aperture is reduced in one stage, so that the clogging of dust is further improved. High reliability.

As described above, the throttle device according to the first embodiment has a highly reliable throttle without clogging of the throttle passage.
As a result, a throttle having a large throttle amount, that is, a throttle having a small diameter can be provided, and the flow velocity of the fluid passing through the throttle can be reduced, so that the fluid flow noise can be significantly reduced.

Further, according to the throttle device according to the first embodiment, the number and the cross-sectional area of the cut grooves 3 formed on the end face of the large-diameter portion 12a of the valve stem 1 are appropriately adjusted, so that the first throttle portion 1 is formed.
3a to the throttle amount in the entire throttle passage can be arbitrarily set.

The large diameter portion 12a and the small diameter portion 12b of the valve stem 1
Instead of forming the cut groove 3 on the step surface 12c with
The valve port 9 of the valve seat 2 facing the step surface 12c
The first throttle portion may be formed between the valve stem 1 and the valve seat 2 by forming a cut groove in the distal end surface portion of the large diameter portion 6a.

The large diameter portion 6a and the small diameter portion 6 of the valve port 9 are
Instead of the step surface 6c between the valve member 1b and the small diameter of the valve stem 1, instead of the step surface 6c, as shown in an enlarged sectional view of a main part of the expansion device according to the modification of the first embodiment in FIG. Part 12
The tapered surface 12f of the valve port 1 contacts the end face of the large diameter portion 6a of the valve port 9 with the tapered surface 6f of the valve port 9 while the tapered surface 12f of the valve port b is tapered. The second constricted portion 13b may be formed by the tapered surface 12f.

With the above-described modified example, the fluid restricted by the second restrictor 13b is supplied to the outlet pipe 1
1 is ejected in a direction inclined with respect to both the axial direction and the radial direction, and the fluid restricted by the second restrictor 13b is discharged from the outlet pipe 1 as in the restrictor of the first embodiment.
As compared with the case of ejecting in the radial direction orthogonal to the axial direction of 1, the cut-out grooves 3 buffer the ejected fluid passing through the second throttle portion 13b and collide with the inner wall surface of the small-diameter portion 6b of the valve port 9. Turbulence, pulsation, and the like of the fluid can be suppressed, and the fluid can be smoothly passed through the second throttle portion 13b, which is advantageous.

Next, the diaphragm device of the second embodiment will be described.
This will be described below with reference to FIGS.

In FIGS. 9 and 10, the same members and portions as those in FIGS. 1 to 5 are denoted by the same reference numerals as those in FIGS.

The throttle device according to the second embodiment shown in a longitudinal sectional view in FIG. 9 changes the valve port 9 in the throttle device according to the first embodiment shown in FIG. 1 to a configuration having only the large-diameter portion 6a. As shown in an enlarged sectional view of a main part in FIG.
Of the small diameter portion 12b of the valve stem 1 corresponding to the connection passage 14 in the expansion device of the first embodiment shown in FIG. And a portion formed by the inner peripheral surface of the large diameter portion 6a of the valve port 9 (corresponding to the inner peripheral surface of the valve port in the claims).
This is another modified example of the first embodiment, in which a second throttle unit 13b that connects the first throttle unit 13a and the outlet pipe 11 is configured.

The diaphragm device of the second embodiment also provides
The same effect as that of the throttle device of the first embodiment can be obtained, and further, since there is no need to form a step in the valve port 9,
The structure can be simplified.

The throttle device of the second embodiment also has a large-diameter portion 12a of the valve stem 1 as in the throttle device of the first embodiment.
Instead of forming the cut groove 3 in the step surface 12c between the small-diameter portion 12b and the small-diameter portion 12b, a cut groove is formed in the distal end surface portion of the large-diameter portion 6a of the valve port 9 of the valve port 2 facing the step surface 12c. Thus, the first throttle portion may be formed between the valve stem 1 and the valve seat 2.

Next, the diaphragm device according to the third embodiment will be described.
This will be described below with reference to FIGS.

In FIGS. 11 and 12, the same members and locations as those in FIGS. 1 to 5 and FIGS.
The same reference numerals as those given in those figures are assigned, and the description of the overlapping portions is omitted.

The throttle device according to the third embodiment shown in the vertical sectional view of FIG. 11 is different from the throttle device of the first embodiment shown in FIG. As shown in an enlarged sectional view of a main part of FIG. 12, a tapered tapered surface 12e (corresponding to an outer peripheral surface portion near the tip of the valve stem in the claims) is formed, and the diaphragm of the first embodiment shown in FIG. A tapered surface 6d corresponding to the tapered surface 12e (corresponding to a valve seat portion located at the opening edge of the valve port in the claims) is formed at a corner on the inner peripheral edge side of the large diameter portion 6a of the valve port 9 in the device. The configuration differs from the aperture device of the first embodiment in that a cut groove 3 having a V-shaped cross section is formed in the tapered surface 6d.

In the throttle device of the third embodiment configured as above, the taper surface 12e of the valve stem 1 comes into surface contact with the tapered surface 6d of the valve port 9 by the valve closing operation of the valve stem 1.
The tapered surface 12e of the valve stem 1 and the cut groove 3 of the valve port 9 form a first throttle portion 13a.
A second throttle portion 13b is formed by 2d and the stepped surface 6c of the large diameter portion 6a and the small diameter portion 6b of the valve port 9.

The tapered surface 12e of the valve stem 1 and the inner peripheral surface of the large diameter portion 6a of the valve port 9 form a connection passage 14 for communicating the first throttle portion 13a and the second throttle portion 13b. A throttle passage is formed by the first throttle portion 13a, the connection passage 14, and the second throttle portion 13b, and the valve chamber 8 and the outlet pipe 11 communicating with the inlet pipe 10 via the throttle passage are closed. Connected in valve state.

Further, in the throttle device of the third embodiment, the throttle passage formed by the first throttle portion 13a, the connection passage 14 and the second throttle portion 13b does not occur due to the valve opening operation of the valve rod 1. Is done.

The diaphragm device of the third embodiment also provides
The same effect as that of the throttle device of the first embodiment can be obtained, and the structure can be simplified because there is no need to form a step at the tip of the valve stem 1.

Further, according to the throttle device according to the third embodiment, the number and the cross-sectional area of the cut grooves 3 formed on the tapered surface 6d of the valve port 9 are appropriately adjusted, so that the first throttle portion 13 is formed.
From a to th, the throttle amount in the entire throttle passage can be arbitrarily set.

By forming a cut groove in the tapered surface 12e of the valve stem 1 facing the tapered surface 6d instead of forming the cut groove 3 in the tapered surface 6d of the valve port 9, the taper of the valve stem 1 is reduced. The first throttle portion may be formed between the surface 12e and the tapered surface 6d of the valve seat 2.

Next, the diaphragm device of the fourth embodiment will be described.
This will be described below with reference to FIGS.

In FIGS. 13 and 14, the same members and locations as those in FIGS. 1 to 5 and FIGS.
The same reference numerals as those given in those figures are assigned, and the description of the overlapping portions is omitted.

The throttle device according to the fourth embodiment shown in the vertical sectional view of FIG. 13 has a tapered surface 12e at the tip end of the valve stem 1 shown in FIG. With the taper surface 12e in surface contact with the tapered surface 6d of the valve port 9 due to the valve closing operation of the valve stem 1, the small diameter portion 6 of the valve port 9 is formed.
In order to avoid buffering with the extended tapered surface 12e, the tapered surface 1 is provided at the corner of the small diameter portion 6b of the valve port 9 on the inner peripheral side.
A tapered surface 6e (corresponding to a stepped port portion in the claims) corresponding to 2e is formed, and the tapered surface 12e of the valve stem 1 facing the tapered surface 6e is spaced apart in the circumferential direction of the valve stem 1. A slit-shaped groove 3 ′ (corresponding to a second groove in the claims) extending from the inside of the distal end portion of the valve stem 1 seated from the distal end surface to the tapered surface 12 e is formed from the distal end surface 12 d of the valve stem 1. The configuration differs from the aperture device of the third embodiment in that it is formed.

In the throttle device of the fourth embodiment configured as described above, the taper surface 12e of the valve stem 1 comes into surface contact with the tapered surfaces 6d and 6e of the valve port 9 by the valve closing operation of the valve stem 1. A first throttle portion 13a is formed by the tapered surface 12e of the valve stem 1 and the cut groove 3 of the valve port 9, and the first throttle portion 13a is formed by the cut groove 3 'of the valve stem 1 and the tapered surface 6e of the valve port 9. A second throttle portion 13b communicating with the outlet pipe 11 is formed, and a throttle passage is formed by the first throttle portion 13a and the second throttle portion 13b, and communicates with the inlet pipe 10 via the throttle passage. The valve chamber 8 and the outlet pipe 11 are connected in a closed state.

In the throttle device of the fourth embodiment, the throttle passage formed by the first throttle portion 13a and the second throttle portion 13b is eliminated by the valve-opening operation of the valve rod 1.

The diaphragm device of the fourth embodiment also provides
The same effect as that of the throttling device of the third embodiment can be obtained, and it passes through the separate second throttling portions 13b formed by the different cut grooves 3 'of the valve stem 1 and the tapered surface 6e of the valve port 9. The flow of the plurality of fluids can be prevented from subsequently colliding at the center of the valve port 9 and causing turbulence.

Further, according to the expansion device according to the fourth embodiment, the cut groove 3 formed in the tapered surface 12e of the valve rod 1 is formed.
By appropriately adjusting the number and cross-sectional area of the second throttle section 13
b to the throttle amount in the entire throttle passage can be arbitrarily set.

Instead of forming the cut groove 3 ′ in the tapered surface 12 e of the valve stem 1 facing the tapered surface 6 e of the valve port 9, as shown in an enlarged sectional view of the main part of FIG. Of the step surface 6c of the large diameter portion 6a and the small diameter portion 6b,
A notch 3 ″ is formed in the tapered surface 6e at the corner on the side of the small diameter portion 6b.
, The second throttle portion 13b may be formed between the tapered surface 12e of the valve stem 1 and the tapered surface 6e of the valve seat 2.

As shown in the enlarged plan view of the main part in FIG. 16, the arrangement of the cut grooves 3, 3 ′, 3 ″ in each embodiment is plurally arranged on a position axially symmetric with respect to the axis of the outlet pipe 11. Further, the position of the cut groove 3 of the first throttle portion 13a formed on the tapered surface 6d of the valve port 9 and the second throttle portion 1 formed on the tapered surface 6e of the valve port 9 are preferable.
The position of the cut groove 3 "of 3b can be shifted in the circumferential direction of the valve stem 1, or the number of cut grooves 3 and the number of cut grooves 3" can be respectively changed.

The arrow in FIG. 16 indicates the flow direction of the fluid flowing from the inlet port 10 into the valve chamber 8.

Although not shown, the shape of the cut grooves 3, 3 ', 3 "in each embodiment is not limited to the above-described semicircular cross section, V-shape, or rectangular shape, and may be any shape.

The throttle device of the present invention is widely applicable as a device for restricting a fluid in a fluid circuit such as a pneumatic circuit or a water circuit, such as a pneumatic circuit or a water circuit. Needless to say.

[0108]

As described above in detail, according to the throttle device of the first aspect of the present invention, the valve stem provided in the valve chamber communicating with the first passage is provided between the valve chamber and the second valve chamber. In a throttle device that comes into contact with and separates from a valve seat of a valve port interposed between the passage and the valve seat, the groove formed in one of the valve stem and the valve seat contacts the valve seat and the valve seat. Forming a first gap between the valve stem and the valve stem, and a second gap communicating with the first gap between the valve stem and the valve port in contact with the valve seat. The first gap and the second gap allow the fluid flowing from the valve chamber to the second passage to form a throttle passage that is gradually reduced in a state where the valve seat and the valve rod are in contact with each other. It was configured.

Therefore, as the valve stem comes into contact with the valve seat, a first groove formed between the valve stem and the valve seat by a groove formed in one of the valve stem and the valve seat. And a second gap formed between the valve stem and the valve port and communicating with the first gap, by a throttle passage continuously formed between the valve chamber and the second passage. Thus, the fluid flowing from the valve chamber to the second passage is throttled in a stepwise manner, so that a larger throttle amount can be obtained in the entire throttle passage.

Moreover, since the throttle amount in each of the first and second gaps can be smaller than the throttle amount in the entire throttle passage, generation of whistling noise due to a sudden change in flow force, It is possible to prevent the generation and the increase of the vibration sound due to the increase and the large load applied to the flow of the fluid.

In addition, while the valve stem is in contact with the valve seat, a first gap formed between the valve stem and the valve seat, and a first gap formed between the valve stem and the valve port. Even if dust and contaminants (dirt) floating in the fluid adhere to and accumulate in the second gap communicating with the gap, the situation where the valve stem opening operation is locked or the fluid passage is blocked may occur. In addition, since the throttle passage is formed by the first and second gaps, the noise level of the flow noise of the fluid is reduced by the biased flow of the fluid acting on the valve stem. Therefore, even if the cross-sectional area of the throttle passage is reduced in order to increase the throttle amount, it is possible to prevent inconvenience in operation and noise reduction.

Further, by appropriately adjusting the number and the cross-sectional area of the grooves formed in one of the valve stem and the valve seat to form the first gap therebetween, the first gap or the throttle is reduced. The throttle amount in the entire passage can be arbitrarily set.

According to the throttling device of the present invention described in claim 2, the valve stem is provided with a large-diameter portion and a small-diameter portion located closer to the distal end of the valve stem than the large-diameter portion. Forming the valve stem such that an end surface of a step portion between the small diameter portion and the large diameter portion comes into contact with the valve seat, and forming the groove in one of the end surface of the step portion and the valve seat. Thus, the first gap is formed between the end face of the step portion and the valve seat.

Therefore, when the stepped end face of the large diameter portion and the small diameter portion provided on the valve stem comes into contact with the valve seat, the gap between the valve seat and the stepped end face of the valve stem in contact with this valve seat is formed. The groove required to form the first gap can be easily formed by a simple process such as cutting the end face of the step portion of the valve stem or the valve seat.

Further, according to the throttling device of the present invention, the valve port has a large-diameter port portion, and the large-diameter port portion is located closer to the second passage than the large-diameter port portion. A small-diameter port portion connected to a large-diameter port portion is provided, and in a state where the end surface of the step portion and the valve seat are in contact with each other, the tip of the small-diameter portion is provided at the end surface of the step port portion between the large-diameter port portion and the small-diameter port portion. The valve port is formed so that the surfaces face at an interval, and the second gap is formed between the end surface of the stepped port portion and the front end surface of the small diameter portion.

Therefore, by appropriately adjusting the dimension of the small diameter portion of the valve stem and the dimension of the large diameter port portion of the valve port in the direction in which the valve stem comes into contact with and separates from the valve seat, the end face of the step portion of the valve stem can be adjusted. A second gap formed between the end surface of the stepped port portion of the large-diameter port portion and the small-diameter port portion provided on the valve port and the distal end surface of the small-diameter portion of the valve rod, The total aperture amount can be set arbitrarily.

According to the throttling apparatus of the present invention, the second gap is formed between the outer peripheral surface of the small diameter portion and the inner peripheral surface of the valve port. ,
By appropriately adjusting the outer diameter of the small diameter portion of the valve stem and the inner diameter of the valve port, when the stepped end face of the valve stem comes into contact with the valve seat, the gap between the inner peripheral surface of the valve port and the outer peripheral surface of the small diameter portion is reduced. The amount of throttle formed in the second gap or the entire throttle passage can be arbitrarily set.

Further, according to the throttling device of the present invention described in claim 5, the valve seat of the valve stem is provided at the valve seat portion of the valve seat located at the opening edge of the valve port. The valve stem and the valve seat are formed such that an outer peripheral surface portion close to the tip contacts, and the groove is formed in one of the valve seat portion and the outer peripheral surface portion, and the valve seat portion and The first gap is formed between the first gap and the outer peripheral surface.

For this reason, when the outer peripheral surface portion near the tip of the valve stem comes into contact with the valve seat portion located at the opening edge of the valve port,
A groove necessary for forming a first gap between the valve seat portion located at the opening edge of the valve port and the outer peripheral surface portion near the distal end of the valve stem in contact with the valve seat portion is formed in the valve port. It can be easily formed by simple processing such as cutting of the valve seat portion located at the opening edge or the outer peripheral surface portion near the tip of the valve stem.

According to the throttling device of the present invention, the valve port has a large-diameter port portion, and the large-diameter port portion is located closer to the second passage than the large-diameter port portion. A small-diameter port portion connected to the large-diameter port portion, and in a state where the valve seat portion and the outer peripheral surface portion are in contact with each other, the valve stem is provided on an end surface of a stepped port portion between the large-diameter port portion and the small-diameter port portion. The valve port is formed so that a front end surface faces at an interval, and the second gap is formed between the step surface end surface and the front end surface of the valve rod.

Therefore, by appropriately adjusting the dimension of the valve stem and the dimension of the large-diameter port portion of the valve port in the direction in which the valve stem contacts and separates from the valve seat, the valve seat portion located at the opening edge of the valve port can be adjusted. When the outer peripheral surface near the tip of the valve stem comes into contact with
A second gap formed between the end surface of the stepped port portion of the large-diameter port portion and the small-diameter port portion provided in the valve port and the outer peripheral surface portion near the tip of the valve stem, or the amount of throttle in the entire throttle passage Can be set arbitrarily.

In the throttling device according to the present invention, the valve port may include a large-diameter port, and the large-diameter port located closer to the second passage than the large-diameter port. A small-diameter port portion connected to the portion, and in a state where the valve seat portion and the outer peripheral surface portion are in contact with each other, the outer peripheral surface portion further contacts a step port portion between the large-diameter port portion and the small-diameter port portion. And the second port formed in one of the step port portion and the outer peripheral surface portion, the valve port is formed between the step port portion and the outer peripheral surface portion. The second gap is formed.

Therefore, by appropriately adjusting the number and the cross-sectional area of the second grooves formed in one of the step port portion of the valve port and the outer peripheral surface portion near the tip of the valve stem. The second gap formed between the rod and the valve port or the throttle amount in the entire throttle passage can be set arbitrarily.

In addition, when the outer peripheral surface near the tip of the valve stem comes into contact with the valve seat portion located at the opening edge of the valve port, the gap between the stepped port portion of the valve port and the outer peripheral surface near the tip of the valve stem. A second groove necessary for forming a second gap therebetween is easily formed by a simple processing such as cutting of a stepped port portion of a valve port or an outer peripheral surface portion near a tip end of a valve stem. Can be.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a throttle device according to a first embodiment of the present invention when a valve is opened.

FIG. 2 is a vertical sectional view of the expansion device of FIG. 1 when a valve is closed.

FIG. 3 is an enlarged sectional view of a main part of a throttle passage portion in FIG. 1;

FIG. 4 is a vertical cross-sectional view showing a state where the throttle passage is clogged when the throttle device of FIG. 1 is closed.

5 is a longitudinal sectional view showing a state in which the blockage of the throttle passage of FIG. 3 is released with the opening of the valve.

FIG. 6 is a longitudinal sectional view showing a diaphragm device having a one-stage diaphragm for comparison with the diaphragm device of FIG. 1;

FIG. 7 is a graph showing a result obtained by experimentally obtaining a relationship between a noise level of a flow noise generated in the throttle device when a gas-liquid two-phase flow is caused to flow through the throttle device and a fluid flow velocity at an outlet of the throttle device. It is.

FIG. 8 is an enlarged sectional view of a main part of a throttle passage portion of a throttle device according to a modification of the first embodiment of the present invention.

FIG. 9 is a vertical cross-sectional view of a throttle device according to a second embodiment of the present invention when a valve is opened.

FIG. 10 is an enlarged sectional view of a main part of a throttle passage portion in FIG. 9;

FIG. 11 is a longitudinal sectional view of a throttle device according to a third embodiment of the present invention when a valve is opened.

FIG. 12 is an enlarged sectional view of a main part of a throttle passage portion in FIG. 11;

FIG. 13 is a longitudinal sectional view of a throttle device according to a fourth embodiment of the present invention when a valve is opened.

FIG. 14 is an enlarged sectional view of a main part of a throttle passage portion of FIG.

FIG. 15 is an enlarged sectional view of a main part of a throttle passage portion of a throttle device according to a modification of the fourth embodiment of the present invention.

FIG. 16 is an enlarged plan view of a main part of a valve seat portion of FIG.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Valve stem 2 Valve seat 3, 3 'Notch groove 4 Valve housing 6a Large diameter part (large diameter port part) 6b Small diameter part (small diameter port part) 6c Step surface (step surface end surface) 6d Tapered surface (valve port opening) 6e Taper surface (step port portion) 8 Valve chamber 9 Valve port 10 Inlet piping (first passage) 11 Outlet piping (second passage) 12 Valve rod 12a Large diameter portion 12b Small diameter portion 12c Step surface (step end surface) 12d Tip surface 12e Tapered surface (outer peripheral surface portion near the tip of valve stem) 13a First throttle portion (first gap) 13b Second throttle portion (second gap) 14 Connection passage DESCRIPTION OF SYMBOLS 31 Electromagnetic coil 32 Guide 33 Plunger 34 Buffer material 35 Spring 37 Valve housing cylindrical part

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hiroo Nakamura 502, Kandachi-cho, Tsuchiura-shi, Ibaraki Pref. Machinery Research Laboratory, Hitachi, Ltd. (72) Atsushi Otsuka 800, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Inside the business department (72) Inventor Hidenori Yokoyama 800 Tomita, Ohira-machi, Shimotsuga-gun, Tochigi Prefecture Inside the cooling division of Hitachi, Ltd. Kisa Komaki 535 Sasai, Sayama City, Saitama Prefecture Sagimiya Manufacturing Co., Ltd.Sayama Plant (72) Inventor Shigetoshi Nakajima 535 Sasai, Sayama City, Saitama Prefecture Sagimiya Manufacturing Co., Ltd.Sayama Plant (72) Inventor Koji Fujisaki Sasaki, Saitama Prefecture 535 Sasai, Ichigo Sagimiya Manufacturing Co., Ltd. Sayama Plant F-term (reference) 3H066 AA01 BA32 BA33 E A15 3H106 DA05 DA13 DA23 DB02 DB12 DB23 DB32 DC02 DC17 DD03 EE20 GB06 GB15 HH03 KK12 KK23 KK34

Claims (7)

[Claims] 1. A throttle device wherein a valve stem provided in a valve chamber communicating with a first passage contacts and separates from a valve seat of a valve port interposed between the valve chamber and the second passage. A groove formed in one of the valve stem and the valve seat forms a first gap between the valve seat and the valve stem in contact with the valve seat, and contacts the valve seat. Between the valve stem and the valve port,
A second gap communicating with the first gap is formed. The first gap and the second gap allow a fluid flowing from the valve chamber to the second passage to pass through the valve seat and the valve. A throttle device, comprising a throttle passage that is reduced in a stepwise manner while in contact with a rod. 2. The valve stem has a large diameter portion and a small diameter portion located closer to the distal end of the valve stem than the large diameter portion, and a stepped end face between the small diameter portion and the large diameter portion is provided. The valve stem is formed so as to be in contact with the valve seat, the groove is formed in one of the step end face and the valve seat, and the groove is formed between the step end face and the valve seat. 2. The aperture device according to claim 1, wherein the first gap is formed. 3. The stepped valve according to claim 1, wherein the valve port is provided with a large-diameter port portion and a small-diameter port portion located on the second passage side of the large-diameter port portion and connected to the large-diameter port portion. The valve port is formed such that a tip end surface of the small-diameter portion faces an end surface of a stepped port portion between the large-diameter port portion and the small-diameter port portion at an interval in a state where the end surface of the small portion contacts the valve seat. 3. The aperture device according to claim 2, wherein the second gap is formed between an end face of the stepped port portion and a tip face of the small diameter portion. 4. The throttle device according to claim 2, wherein the second gap is formed between an outer peripheral surface of the small diameter portion and an inner peripheral surface of the valve port. 5. The valve stem and the valve stem such that an outer peripheral surface portion of the valve stem near an end of the valve stem comes into contact with a valve seat portion of the valve seat located at an opening edge of the valve port. The valve seat is formed, and the groove is formed in one of the valve seat portion and the outer peripheral surface portion to form the first gap between the valve seat portion and the outer peripheral surface portion. Claim 1
The squeezing device as described. 6. The valve according to claim 6, wherein the valve port is provided with a large-diameter port portion and a small-diameter port portion located on the second passage side of the large-diameter port portion and connected to the large-diameter port portion. In a state where the seat portion and the outer peripheral surface portion are in contact with each other, the valve port is formed such that a distal end surface of the valve stem faces an end surface of a stepped port portion between the large-diameter port portion and the small-diameter port portion at an interval. 6. The expansion device according to claim 5, wherein the second gap is formed between an end surface of the stepped port portion and a front end surface of the valve stem. 7. The valve according to claim 7, wherein the valve port is provided with a large-diameter port portion and a small-diameter port portion located on the second passage side of the large-diameter port portion and connected to the large-diameter port portion. In a state where the seat portion and the outer peripheral surface portion are in contact with each other, the valve port is formed so that the outer peripheral surface portion further contacts a step port portion between the large-diameter port portion and the small-diameter port portion; 6. The aperture according to claim 5, wherein the second gap is formed between the stepped port portion and the outer peripheral surface portion by a second groove formed in one of the port portion and the outer peripheral surface portion. apparatus.