JPH0561505B2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a high differential pressure and minute flow rate reducing valve, and in particular, the present invention relates to a pressure reducing valve with a high differential pressure and a small flow rate. The present invention relates to a pressure reducing valve that inhales fluid and causes it to reciprocate using the pressure difference generated between both ends of the valve body, and controls the flow rate sent by this reciprocating movement by the amount of reciprocating movement (stroke) and rotational speed of the valve body.

[Prior Art] Generally, a needle valve is used as a valve in which a high differential pressure suppresses a minute flow rate.

[Problems to be Solved by the Invention] However, in this type of control valve, the port with a large pressure difference is formed with a small diameter, so the flow path may become clogged due to the introduction of foreign matter, and depending on the liquid handled, the flow rate may be reduced. However, it has the disadvantage that cases of instability often occur.

Therefore, it is an object of the present invention to alternately suck handling liquid into each valve chamber at both ends of the valve body by rotationally driving a cylindrical valve body, and to reduce the valve pressure by the pressure difference generated at both ends of the valve body. By reciprocating the body and adjusting the stroke amount, the port diameter can be set to any desired size regardless of the pressure difference, making it possible to stabilize the flow rate and control the flow rate over a wide range. The object of the present invention is to provide a pressure reducing valve that can achieve a high differential pressure and a small flow rate.

[Means for Solving the Problem] In order to achieve the above object, the present invention includes a valve chamber in which an inlet and an outlet are provided on opposite sides of a cylindrical chamber, and a rotary and axial valve in the valve chamber. A cylindrical valve body that is slidably inserted and has a point-symmetric notch extending from a predetermined position on the side surface to each end, and a regulating means that adjustably regulates the axial stroke of the valve body. and a drive unit connected to one end of the valve body to rotationally drive the valve body, and the stroke amount and rotation speed of the valve body that reciprocates due to the pressure difference between the two ends of the valve body generated by the rotational drive of the valve body. The feature is that the flow rate is controlled by.

On the other hand, in the present invention, a cylindrical chamber has a valve chamber provided with an inlet and an outlet on opposite sides, and a pair of predetermined predetermined valve chambers fitted in the valve chamber so as to be rotatable and slidable in the axial direction. A cylindrical valve body that forms a width notch and has a bent communication path that communicates from the notch to each end, and a regulating means that adjustably regulates the axial stroke of the valve body. and a drive unit connected to one end of the valve body to rotationally drive the valve body, and the flow rate is controlled by the stroke amount of the valve body that reciprocates based on the pressure difference between the two ends of the valve body generated by the rotational drive of the valve body. It is characterized by

In this case, it is preferable that the valve body is configured such that its sliding portion is slidably connected to the output shaft of the drive portion in the axial direction.

Further, the valve body may be configured to be integrally connected to a rotor of a canned motor.

[Operation] According to the high differential pressure minute flow rate reducing valve according to the present invention,
One notch communicates with the valve chamber that seals the handled liquid that has flowed into the valve chamber at one end due to the rotational drive of the valve body, and the other notch communicates with the empty valve chamber at the other end. When the two sections are indexed to the suction port, the high-pressure side handling liquid flows into the empty valve chamber at the other end through the other notch indexed toward the suction port, and the valve body is moved in the axial direction to move the valve body to the one end. The liquid in the valve chamber is compressed and discharged from the discharge port on the low pressure side. In this case, the amount of discharge from the pressure reducing valve can be adjusted by adjusting the stroke amount of the valve body.

When the valve body is then rotated, the valve chambers at both ends of the valve body are hermetically sealed, and when the valve body is further rotated and the positional relationship of the notches is reversed, the valve body moves in the opposite direction. As the rotation continues, the valve body alternately reciprocates, thereby making it possible to send a controlled amount of liquid.

[Example] Next, an example of the high differential pressure minute flow rate reducing valve according to the present invention will be described in detail below with reference to the accompanying drawings.

FIG. 1 is a sectional view of a pressure reducing valve showing a first embodiment of the present invention, in which the valve body is connected so as to be slidable in the axial direction via an output shaft of a drive unit that rotationally drives the valve body and an intermediate shaft. It is something.

Further, FIG. 2 is a cross-sectional view of a pressure reducing valve showing a second embodiment, in which a valve body is integrally connected to a rotor of a canned motor and configured to be rotatable and movable in the axial direction together with the rotor.

That is, in FIG. 1, reference numeral 10 denotes a cylindrical valve body that is slidably and rotatably fitted in a cylindrical chamber 14 formed in a casing 12, and is located at a predetermined position on the side surface of the valve body 10. A pair of notches 16a and 16b extending from the bottom to the respective ends are formed point-symmetrically.

Further, a motor 20, which is a drive unit, is attached to the lower end of the casing 12 via a housing 18, and an intermediate shaft 22 is rotatably supported within the housing 18 by bearings 24a, 24b.

This intermediate shaft 22 is configured such that its lower end is connected to the output shaft 26 of the motor 20 via a coupling 28, and its other end upper end is axially slidably connected to the lower end of the valve body 10. .

In this case, an engagement hole 30 for connection is formed in the lower part of one end of the valve body 10 in the axial direction, and the cross section of this hole 30 is, for example, square or hexagonal. A shaft 32 of the same shape formed at the upper part of the other end of 22 is engaged so as to be slidable in the axial direction.

Note that the engagement hole 30 and the shaft 3 that engages with it
In addition to the above, a key or a spline may be used for the cross-sectional shape of No. 2 as long as it has the function of sliding in the axial direction and rotatably engaging.

On the other hand, in the cylindrical chamber 14 formed inside the casing 12, an inlet 34 and an outlet 36 communicating with the outside are provided on opposite sides.

This cylindrical chamber 14 is formed to have a dimension expanded in the axial direction with respect to the entire length of the valve body 10 to be inserted therein, and is further provided with an upper portion of the valve body 10 on the side opposite to the intermediate shaft 22 side. A stroke adjustment screw 40 is screwed into the casing 12 and is a regulating means having a contact portion 38 at the tip thereof that contacts the upper end of the valve body 10 to adjust the stroke amount.

Furthermore, within the cylindrical chamber 14, valve chambers 42a and 42b are formed on both end surfaces of the cylindrical valve body 10 that is inserted into the chamber, and a valve body 1 is formed in each valve chamber.
Notches 16a and 16b formed symmetrically at point 0
are configured so that they communicate.

As a result, as shown in FIG.
When the handling liquid on the high pressure side flows into the lower valve chamber 42b in the flow shown by the arrow in the figure,
The handling liquid already sealed in the upper valve chamber 42a is discharged from the low pressure outlet 36 through the notch 16b facing the outlet 36 by the action of the hydraulic pressure flowing into the lower valve chamber 42b.

Next, a second embodiment of the pressure reducing valve of the present invention will be described in detail with reference to FIG.

For convenience of explanation, the same reference numerals are given to the same components as in the first embodiment described above, and detailed explanation thereof will be omitted.

That is, the canned motor 46 is directly attached to one end of the casing 12, and the canned motor 46 is directly attached to one end of the casing 12.
The lower end of one end of the valve body 44 inserted into the chamber 14 in the canned motor 46 is integrally connected to the rotor shaft 50 of the canned motor 46. The rotor 48 is inserted into the internal chamber of the stator 52 with a gap formed therein, and the internal chamber of the stator 52 communicates with the chamber 14 .

Therefore, the handling liquid on the high pressure side flowing in from the suction port 34 flows through one notch 16a of the valve body 44 along the arrow in FIG. 2, and then passes between the rotor 48 and the stator 52. and flows into the stator internal chamber. As a result, the rotor 48, which is movable in the axial direction, rises due to the inflowing hydraulic pressure, and is sealed in the valve chamber 42a above the valve body 10 by the rising action of the valve body 10, which is integrally connected to the rotor 48. The handling liquid is discharged from the low pressure side discharge port 36.

In this case, the stroke amount of the valve body 44 in the axial direction is regulated by the contact between the tip of the stroke adjustment screw 40 above the valve body 44 and a fixed stopper 54 provided in the rear chamber of the canned motor 46.

The valve body 10 is rotated by the drive source while moving in the axial direction, and when the valve body 10 makes a half turn (180°) within the chamber 14, the notch 16a facing the suction side is closed to the discharge side. The notch 16 rotated toward the outlet 36 and faced the outlet 36 at the same time.
b rotates toward the suction port 34 side.

However, due to the rotation of the valve body 10, the notches 16a, 1
The vertical positional relationship of the valve chamber communicating with 6b is reversed, and the high-pressure handling liquid that has flowed from the suction port 34 into the valve chamber 42a located above the valve body 10 flows through the notch 16b.

Therefore, the valve body 10 is lowered under the action of this handling liquid, and the handling liquid in the valve chamber 42b is discharged from the low-pressure side discharge port 36 through the notch 16a facing the discharge side.

That is, the operating state of this valve body is as shown in Fig. 3a-
This is clear from the operational exploded views shown in FIGS. 4d and 4a to 4d.

First, the states shown in FIGS. 3a and 4b are as follows:
The lower notch 16a of the cylindrical valve body 10 and the upper notch 16b provided point-symmetrically thereto face the high-pressure side inlet 34 and the low-pressure side outlet 36 of the casing 12, respectively.

When high-pressure handling liquid flows in from the suction port 34 in this state, this handling liquid flows through the notch 16a of the valve body 10 and flows into the valve chamber 42b below the valve body, and this liquid pressure causes the valve body 10 to flow into the valve chamber 42b. raise.

Due to this upward movement of the valve body 10, the handling liquid that has been in the valve chamber 42a above the valve body flows through the notch 16b of the valve body 10 and flows out from the discharge port 36 on the low pressure side.

Note that the stroke length of the movement of the valve body 10 in this case is regulated by the stroke adjustment screw 40, and the flow rate can be controlled by adjusting this stroke.

Next, the states shown in FIGS. 3b and 4b are as follows:
The valve body 10 is rotated by the intermediate shaft 2 by the rotational drive of the motor 20.
2, the empty valve chamber 42a and the valve chamber 42b into which the high-pressure handling liquid has entered are connected to the side wall surface of the cylindrical chamber 14 and the outer peripheral surface of the valve body 10, respectively. It becomes more tightly sealed.

At the same time, the suction port 34 and the discharge port 36 are closed by the outer peripheral surface of the valve body 10.

Furthermore, the states shown in FIGS. 3c and 4c show a state in which the valve body 10 has been rotated by 180 degrees, and the positions of the notches relative to the suction port 34 and the discharge port 36 are respectively changed.

That is, the empty upper valve chamber 42a is connected to the suction port 34 side, and the lower valve chamber 4, which is filled with high-pressure handling liquid, is connected to the suction port 34 side.
2b rotates toward the low-pressure side discharge port 36, and the valve body 10 is moved to the intermediate shaft 22 under the action of the high-pressure handling liquid that has flowed into the empty valve chamber 42a from the suction port 34.
By this movement, the handled liquid in the valve chamber 42b is discharged from the discharge port 36 on the low pressure side.

Subsequently, the state shown in FIG. 3 d and FIG.
a and the empty valve chamber 42b are respectively hermetically sealed.

Next, a third embodiment of the pressure reducing valve will be described with reference to FIG.

For convenience of explanation, the same reference numerals are given to the same components as in the first and second embodiments described above, and detailed explanation thereof will be omitted.

That is, in this embodiment, the sealing performance is improved by changing the notch of the valve body of the previous embodiment.

In the cross-sectional view of the pressure reducing valve shown in FIG. 4, a pair of parallel notches 1 are formed on both sides of a substantially central portion of a valve body 11 that is fitted into a cylindrical body 14 so as to be slidable in the axial direction.
7a, 17b are formed, the width of which in the axial direction is at least within the range of the maximum stroke length of the valve body 14.

Further, the valve body 14 has the notches 17a, 17.
Communication passages 54a and 54b are provided at b, which are bent from the radial direction to the axial direction and communicate with the respective ends of the valve body 14.

Therefore, these communication paths 54a and 54b are connected to room 1.
4 and communicate with valve chambers 43a and 43b formed by each end of the valve body 11, respectively.

A pair of notches 1 formed in the valve body 11
The outer peripheries on both sides of the valve chambers 7a and 17b are sealed by, for example, an O-ring 56, so that the handled liquid flowing into each of the valve chambers 43a and 43b can be reliably sealed.

Note that the flow rate Q passing through this pressure reducing valve is
The stroke length (reciprocating distance) of 0 or 11 is L, the diameter of valve body 10 or 11 is D, and the rotation speed is N.
Then, it can be expressed as Q=πD ²・L・N/4 (1).

Therefore, the flow rate can be adjusted by changing the stroke length or the rotation speed of the motor using the stroke adjustment bolt.

[Effects of the Invention] As is clear from the above-mentioned embodiments, the high differential pressure and small flow rate reducing valve according to the present invention rotates the cylindrical valve body to alternately drive the pressure inside each valve chamber at both ends of the valve body. By sucking in the liquid to be handled and making use of the pressure difference generated between the two ends of the valve body to perform reciprocating motion and adjust the stroke amount, the set pressure or pressure fluctuation on the primary and secondary sides can be controlled. A constant flow rate can be delivered regardless of the amount of liquid, and since the flow path area can be increased, there is no valve clogging due to foreign matter, and stable liquid delivery can be achieved.

In addition, if an abnormality occurs in the system and the drive motor stops, fluid delivery is also blocked, making it safe.
Since the flow rate can be controlled using both the stroke length and rotation, it is possible to control the flow rate over a wide range.

Furthermore, since the flow rate is proportional to the stroke length and the rotational speed, proportional control becomes easy, and many other excellent effects are achieved.

Although the preferred embodiments of the present invention have been described above, the structure of the pressure reducing valve of the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the spirit of the present invention. Of course.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of a pressure reducing valve showing a first embodiment of the high differential pressure and minute flow rate reducing valve of the present invention, FIG. 2 is a sectional view of a pressure reducing valve showing a second embodiment, and FIG. 3a ~d
is an exploded view of valve operation, and Figures 4 a to d are A- in Figure 3.
FIG. 5 is a cross-sectional view of a pressure reducing valve showing a third embodiment. 10, 11, 44... Valve body, 12... Casing, 14... Chamber, 16a, 16b, 17a, 1
7b...Notch, 18...Housing, 20...
Motor, 22... Intermediate shaft, 24a, 24b... Bearing, 26... Output shaft, 28... Coupling, 3
0...Engagement hole, 32...Shaft, 34...Suction port, 3
6... Discharge port, 38... Contact portion, 40... Stroke adjustment screw, 42a, 42b... Valve chamber, 46...
... Canned motor, 48 ... Rotor, 50 ... Rotor shaft, 52 ... Stator, 54 ... Stopper,
56a, 56b...Communication path, 58...O ring.

Claims (1)

[Scope of Claims] 1. A valve chamber with an inlet and a discharge port provided on opposite sides of a cylindrical chamber, and a valve chamber that is rotatably and slidably slidable in the axial direction and inserted into the valve chamber from a predetermined position on the side to each end. a cylindrical valve body with a point-symmetrical notch extending to the bottom; a regulating means for adjustablely regulating the axial stroke of the valve body; A high differential pressure minute flow rate reduction device comprising a connected drive unit, and the flow rate is controlled by the stroke amount and rotational speed of the valve body that reciprocates based on the pressure difference between the two ends of the valve body caused by the rotational drive of the valve body. valve. 2. A valve chamber with an inlet and a discharge port provided on opposite sides of a cylindrical chamber, and a pair of notches of a predetermined width on both sides of the valve chamber, which are rotatably and slidably inserted into the valve chamber at the center thereof. a cylindrical valve body having a bent communication path communicating from the notch to the separate ends; a regulating means for adjustablely regulating the axial stroke of the valve body; and a drive unit connected to one end of the valve body to rotationally drive the valve body, and the flow rate is controlled by the stroke amount and rotational speed of the valve body that reciprocates based on the pressure difference between the two ends of the valve body generated by the rotational drive of the valve body. A pressure reducing valve with high differential pressure and small flow rate. 3. The high differential pressure, small flow rate pressure reducing valve according to claim 1 or 2, wherein the sliding portion of the valve body is axially slidably connected to the output shaft of the drive portion. 4. The high differential pressure minute flow pressure reducing valve according to claim 1 or 2, wherein the valve body is integrally connected to a rotor of a canned motor.