JP5185982B2 - Flow control valve - Google Patents

Description

  The present invention relates to a flow control valve.

As a flow control valve, there is a throttle valve (normally without pressure compensation) that regulates the flow rate by changing the cross-sectional area of the flow path with a throttle. As shown in FIG. 12 , this throttle valve has a needle valve (valve element) 2 accommodated in a body 1 and is accommodated in a freely reciprocating manner by a threaded portion 2b formed on a valve shaft 2a. The flow rate is adjusted by changing the annular cross-sectional area between the surface 2d and the valve seat 3. This throttle valve has features such as a simple structure and low cost, and is applicable to a high-pressure hydraulic circuit.

  The adjustment of the flow path area is mainly performed by adjusting the manual handle 4 fixed to the upper end of the valve shaft 2a of the needle valve 2, and the operation is simple. The confirmation of the closed state is made by sensing the frictional force when the operator turns the manual handle 4 and the tapered surface 2d of the needle valve 2 comes into pressure contact with the valve seat 3. Accordingly, such a throttle valve has a very simple structure under a manual operation and has a stable performance, and thus is used in many fields.

As a method for electrically adjusting the flow passage area of the throttle valve having such a structure, a system in which an electric motor is attached and driven instead of the manual handle 4 of the needle valve 2 is employed.
In addition, as a needle valve using an electric motor, a spring is provided between a washer provided at the upper end of the valve shaft of the needle valve and a valve body that supports the valve shaft, and at the upper end surface of the valve shaft. The output shaft of the linear motor that slides in the axial direction is brought into contact with the tip surface of the linear motor, and when the valve is closed, the spring is compressed by moving the linear motor's output shaft closer to the valve seat to compress the needle. The taper surface of the valve is pressed against the valve seat, and when the valve is opened, the output shaft is moved away from the valve seat, and the needle valve is moved in the valve opening direction by following the output shaft by the spring force of the spring. There has been proposed a needle valve that separates the valve from the valve seat (for example, see Patent Document 1).

JP 2006-153205 A (page 4-5, FIG. 1)

  As a method for electrically adjusting the flow passage area of the throttle valve having the structure as shown in FIG. 12, in a system in which an electric motor is attached and driven instead of the manual handle 4 of the needle valve 2, the valve is opened and closed. There was a great drawback in that the degree of freedom in controlling the valve was low, and the seat point (control position) was shifted with the passage of time (change over time). In particular, the positioning of the valve closing position results in a control system that can only find positioning means that creates an overload condition. That is, the confirmation of the valve closing state is determined by sensing the frictional force when the operator turns the manual handle 4 and the tapered surface 2d of the needle valve 2 is pressed against the valve seat 3 in manual operation. When an electric motor is used, the needle valve 2 is excessively tightened and is brought into pressure contact with the valve seat 3 to be closed, which causes an overload state of the electric motor, and the electric motor and control system. This is a cause of failure such as overcurrent.

Further, the actual flow rate control valve of the needle valve system is not actually adapted to power assist, pressure balance, and flow force from the viewpoint of original use, that is, from the viewpoint of manual operation. Technically, there is a method of applying power assist or a pressure balance mechanism, but the shape becomes extremely large, and it is technically difficult to cope with the flow force in terms of shape.
When the flow force is not dealt with, vibration due to pulsation of the fluid is generated, and accordingly, vibration is generated in a backlash portion such as a gear, which causes unstable positioning control. For this reason, it is necessary to apply a reverse force against the flow force. This flow force has a high fluid pressure and increases in accordance with the flow rate, and it is necessary to apply power assist and a pressure balance mechanism. However, if no power assist or pressure balance mechanism is provided, the flow force requires more operating force (driving force / stopping force) for positioning control, and the electric motor and control system become larger and costly. Become. Therefore, if the response to the flow force is not made, an unstable factor occurs in the flow control of the high-pressure and large-flow rate fluid in the control by the electric motor as well as the control by the manual operation.

  Further, in the needle valve type electric control, the displacement of the needle valve in the axial direction (lift) is required, and in order to absorb this displacement, the valve shaft and the electric motor are combined with a spline mechanism or a mechanism comparable to this. Need to be connected. For this reason, backlash due to clearance occurs in both of these mechanisms and the needle valve feed screw, that is, it becomes difficult to accurately fix the needle valve to the target position, which causes a lack of reproducibility. It is also.

  Further, the needle valve disclosed in Patent Document 1 has a complicated structure, which increases the number of parts, makes assembly difficult, and is expensive. In addition, an O-ring is provided in the control fluid passage circuit, and it is necessary to periodically replace the O-ring. Furthermore, it is difficult to use it for fluid control of high pressure and large flow rate because of its structure. Also, no response to the flow force has been made, and problems similar to those of the throttle valve shown in FIG.

Also, structurally, in the flow rate control, especially in the control for quantitatively changing the passage area, the direct acting spool mechanism is generally used, but the dimension management between the spool and the land, drilling, cylindricity, straightness, etc. Special equipment and technology are required every time, and the cost remains high.
The object of the present invention is to divide the flow between input and output of the fluid into two to cancel the flow force, and to create a consolidated state between the sliding parts by using the source pressure side of the control fluid as a back pressure so that the fluid from the contact portion It is an object of the present invention to provide a flow rate control valve that can prevent the leakage of the fluid and keeps it rotatable, and can change the passage area of the fluid continuously and smoothly with a simple structure.

In order to solve the above-described problem, a flow control valve according to claim 1 of the present invention includes:
The first flow path and the second flow path are provided so as to penetrate from one end face to the other end face, and these first flow path and second flow path are on both sides of a straight line passing through the center. A stator that is symmetrically arranged and has one opening on the one end face, and is bifurcated inside to form two openings on the other end face;
One end face is in close contact with the other end face of the stator and is rotatable, and the first flow path and the second flow path are blocked at the first control position on the one end face. As the first control position is rotated from the first control position to the second control position, the corresponding openings on the one side of the two openings of the first flow path and the second flow path A rotor provided with a first communication groove and a second communication groove for communicating the corresponding openings on the other side with the first flow path and the second flow path;
A casing for housing the stator and the rotor;
A pressing means is provided between the end surface on the other side of the rotor and the casing, and presses the end surface on the one side of the rotor against the end surface on the other side of the stator.

  The fluid that has flowed in from one opening of the first flow path of the stator is divided into two branches inside, and flows into the first and second communication grooves of the opposing rotor from the two openings. In the first control position of the rotor, the first flow path and the second flow path of the stator are blocked. Thereby, the flow control valve is closed. As the rotor is rotated from the first control position to the second control position, the first communication groove and the second communication groove of the rotor are connected to the two openings facing the first flow path of the stator and the second. The fluid flows into the two openings of the second flow path from the two openings of the first flow path of the stator in communication with the two openings facing each other, and merges inside the stator to form one Discharge from the opening. Thereby, the flow control valve is opened. At this time, the fluid flowing through the first communication groove and the second communication groove of the rotor flows in a direction in which the flow force is canceled when viewed from the center axis symmetry. Thereby, the vibration resulting from the pulsation of the fluid is also reduced, and positioning control becomes easy.

  The rotor is in close contact with the stator and rotatably supported by pressing means that is contracted in a space between the housing and the opposite end surface that is in close contact with the stator. Then, the first flow path and the second flow path are blocked or communicated by the rotation of the rotor. That is, the flow control valve is closed or opened. Accordingly, it is possible to open and close the flow control valve by rotating the rotor only by an electric operation corresponding to the function without using power assist such as hydraulic pressure or air pressure. As a result, it is possible to easily cope with a hydraulic circuit having a high pressure and a large flow rate.

A flow control valve according to claim 2 of the present invention is the flow control valve according to claim 1,
Each of the two openings of the first and second flow paths opening on the other end face of the stator is disposed on the same circumference,
The first and second communication grooves of the rotor are characterized in that at least both ends are arranged on the same circumference facing the two openings of the first and second flow paths.

The two openings of the first and second flow paths of the stator are arranged on the same circumference, and at least both ends of the first and second communication grooves of the rotor are the first and second flow paths of the stator. The first flow path and the second flow path can be blocked or communicated with each other by disposing them on the same circumference facing the two openings of the path and rotating the rotor.
A flow control valve according to claim 3 of the present invention is the flow control valve according to claim 1 or 2,
The pressing means includes a spring contracted between an end face on the other side of the rotor and an end face facing the casing;
Provided in the rotor, each one end is opened to the bottom surface of each of the first and second communication grooves, and each other end is opened to the other end surface, so that each communication groove side to the other end surface side It is characterized by comprising a one-way valve that allows the flow of fluid only to the head.

A back pressure (back pressure) is applied by supplying a fluid pressure through a one-way valve from the communicating groove side to the space between the rotor and the casing, with a spring contracted in the space between the rotor and the casing. The mechanical frictional force between the rotor and the casing is reduced, and the rotor can be rotated with a small driving force while maintaining the compacted state between the end face of the stator and the end face of the rotor.
A flow control valve according to claim 4 of the present invention is the flow control valve according to claim 1 or 2,
The pressing means includes a spring contracted between an end face on the other side of the rotor and an end face facing the casing;
When one of the first flow path and the second flow path of the stator is used as a fluid inlet, and the other is used as a fluid outlet, the communication groove on the side where the fluid can be introduced to the communication groove when the valve is closed. One end is opened on the bottom surface, and the other end is opened on the other end surface of the rotor, and is composed of a flow path for supplying a part of the fluid.

  A stator that is contracted in a space portion between the rotor and the casing, and a back pressure (back pressure) is applied by supplying fluid pressure through the flow path from the communication groove side to the space portion between the rotor and the casing. And the opposite surfaces of the rotor are pressed into a compacted state and the rotor can be rotated. As a result, the flow control valve can be driven to open and close only by an electric operation without using power assist such as hydraulic pressure or air pressure.

  According to the present invention, the flow path between the input and output of the stator is divided into two, and the fluid input from the first flow path flows in the opposite direction by the two communication grooves provided in the rotor and flows into the second flow path. By doing so, the flow force can be canceled and positioning control becomes easy. Further, the configuration of the flow control valve is simple, the assemblability is good, and the cost can be reduced.

  In addition, the back pressure (back pressure) is applied to the rotor using the fluid pressure in cooperation with the spring to reduce the friction between the rotor and the casing caused by the mechanical spring mechanism, and between the stator and the rotor. The pressure on the contact surface can be increased to create a consolidated state to prevent fluid leakage from the contact portion and can be driven only by electric operation without using power assist such as hydraulic pressure or air pressure. Therefore, it can be applied to a high pressure, large flow rate hydraulic circuit.

It is sectional drawing of the flow control valve which concerns on this invention. FIG. 2 is an end view of the stator as viewed from the direction of arrow II of the flow control valve meter shown in FIG. 1. FIG. 3 is an end view of the stator as seen from the direction of arrow III-III of the flow control valve shown in FIG. 1. FIG. 4 is an end view of the rotor as viewed from the direction of arrow IV-IV of the flow control valve shown in FIG. 1. FIG. 2 is an explanatory diagram showing a relationship between first and second flow paths of a stator and first and second communication grooves of a rotor when the flow control valve shown in FIG. 1 is closed. FIG. 6 is an explanatory diagram showing a relationship between the first and second flow paths of the stator and the first and second communication grooves of the rotor when the flow control valve shown in FIG. 5 is opened. It is explanatory drawing which shows the change of the opening area between the communicating groove of the rotor shown in FIG. 5, and the opening part of the flow path of a stator. It is explanatory drawing which shows the modification which shows the change of the opening area between the communicating groove | channel of a rotor, and the opening part of the flow path of a stator. It is the circuit diagram which showed the flow control valve shown in FIG. 1 systematically. It is the circuit diagram which showed the modification of the flow control valve shown in FIG. 1 systematically. It is the circuit diagram which showed the modification of the flow control valve shown in FIG. 1 systematically. It is sectional drawing which shows an example of the conventional flow control valve (needle valve).

  Hereinafter, a flow control valve according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a schematic configuration of a flow control valve of the present invention. A flow control valve 10 accommodates a stator (fixed portion) 11 as a control valve main body, a rotor (rotating portion) 12 as a valve body, and these. And a pressing means 14 provided between the rotor 12 and the casing 13 for pressing the rotor 12 so as to be in close contact with the stator 11.

  As shown in FIGS. 1 to 3, the stator 11 has a cylindrical shape, and is symmetrically arranged on the left and right sides of a straight line α indicated by a one-dot chain line passing through the center O when viewed from the one end face 11 a side. And the second flow path 22 is provided so as to penetrate from the end surface 11a on one side to the end surface 11b on the other side. And these 1st flow paths 21 and 2nd flow paths 22 are bifurcated inside as shown by a dotted line in FIG.1 and FIG.2. The first flow path 21 and the second flow path 22 have one opening 21A and an opening 22A on the end face 11a, respectively, and two openings 21a and 21b and openings 22a and 22b on the end face 11b, respectively. It is open. Female screws (not shown) are formed on the inner peripheral surfaces of the openings 21A and 22A so that they can be connected to a pipe joint.

  As shown in FIGS. 2 and 3, the openings 21A and 22A and the two openings 21a and 21b and the openings 22a and 22b of the first channel 21 and the second channel 22 are on the same circumference. Is arranged. As shown in FIG. 3, the two openings 21a and 21b of the first flow path 21 are arranged at predetermined angles, for example, at a central angle of 45 degrees on both sides of the opening 21A indicated by the dotted line, In this case, the two openings 22a and 22b of the second channel 22 are also arranged at a central angle of 45 degrees on both sides of the opening 22A indicated by the dotted line. That is, the openings 21a and 21b and the openings 22a and 22b are arranged at equal intervals on the same circumference at a central angle of 90 degrees along the circumferential direction. Accordingly, the openings 21a and 22a and the openings 21b and 22b are arranged at symmetrical positions on both sides of the straight line α passing through the center O.

  Further, as shown in FIG. 3, a positioning shaft hole 11c for determining the rotation center position of the rotor 12 is provided at the center position of the end surface 11b of the stator 11, and the rotation of the rotor 12 is performed at a predetermined position near the outer peripheral portion. A positioning groove 11d for restricting a moving position, that is, a valve closing position and a valve opening position, which will be described later, is provided concentrically with the openings 21a, 21b, 22a, and 22b to have a predetermined length. Yes.

  As shown in FIG. 1, the rotor 12 has a cylindrical shape with the same diameter as the stator 11, and the first end surface 12 a that is in close contact with the end surface 11 b of the stator 11 has a first position corresponding to the rotation position as shown in FIG. 4. Two communication grooves 23 and a communication groove 24 that can communicate with the corresponding openings 21 a and 22 a and the openings 21 b and 22 b of the flow path 21 and the second flow path 22 are provided. A rotation shaft 15 is provided at the center position of the end surface 12 b on the other side of the rotor 12. The communication groove 23 is arranged on the same circumference corresponding to the opening 21a and the opening 21b, and the communication groove 24 is arranged on the same circumference corresponding to the openings 22a and 22b. The shape is a symmetrical shape. In FIG. 4, the communication groove 23 shows a state in which the openings 21a and 22a are connected, and the communication groove 24 shows a state in which the openings 21b and 22b are in communication.

  The communication groove 23 communicates with the opening 21a when the valve shown in FIG. 5 is closed, and communicates with the corresponding opening 21a and the opening 22a when the valve is opened as shown in FIG. The communication groove 24 communicates with the opening 22b when the valve shown in FIG. 5 is closed, and communicates with the corresponding opening 22b and the opening 21b when the valve shown in FIG. 6 is opened. The communication groove 23 forms a plane in which an end surface 23a on one side communicating with the opening 22a circumscribes the opening 22a.

  Since the end surface 23a is thus flat, the opening area of the opening 22a can be changed as shown by a two-dot chain line in accordance with the rotation of the rotor 12 indicated by an arrow as shown in FIG. It becomes. Furthermore, by making the shape of the opening 22a substantially trapezoidal along the circumferential direction as shown in FIG. 8, the opening area can be changed in proportion to the rotation of the rotor 12 as shown by a two-dot chain line. It becomes. The same applies to the communication groove 24. Note that the end surfaces 23a and 24a on one side of the communication grooves 23 and 24 may be curved like the end surfaces 23b and 24b on the other side. Further, the shape of each opening is not limited to the circular shape or the substantially trapezoidal shape described above, and may be other shapes.

Further, the communication groove 23 communicates the corresponding opening 21a and the opening 22a, and the communication groove 24 only needs to communicate the corresponding opening 21b and the opening 22b. It is not necessary and may be formed in a straight line as shown by a two-dot chain line in FIG.
As shown in FIGS. 1 and 4, a positioning shaft hole 12 c is provided at the center position of the end surface 12 a of the rotor 12 so as to face the positioning shaft hole 11 c of the stator 11. Approximately half of the pin (rotating shaft) 25 is rotatably inserted into the shaft hole 12c, and approximately half protrudes. Further, as shown in FIG. 4, the rotor 12 is opened at the position corresponding to the positioning groove 11d provided on the end surface 11b of the stator 11 shown in FIG. A positioning pin 26 is provided that can slide to a position.

  As shown in FIGS. 1 and 4, the rotor 12 has a predetermined position on the bottom surface of the communication grooves 23, 24, for example, between the communication groove 23, 24 side and the end surface 12 b side between the substantially central position and the end surface 12 b. One-way valves (check valves) 16 and 17 that allow fluid flow are provided. The end surface 11b of the stator 11 and the end surface 12a of the rotor 12 are precisely surface-treated so that the end surface 12a of the rotor 12 can be rotated with the end surface 11b of the stator 11 being in good contact with the end surface 11b. Yes.

  The casing 13 has a bottomed cylindrical shape, the rotor 12 is rotatably accommodated with a very small clearance, and a shaft hole 13b through which the rotary shaft 15 of the rotor 12 is inserted in the center of one end surface 13a. Is provided. The rotor 12 is rotatably inserted into the casing 13 via the O-ring 28, the rotating shaft 15 protrudes from the shaft hole 13 b of the casing 13, and is supported and accommodated in a liquid-tight manner by the O-ring 27. Yes. A plurality of, for example, four, disc springs 18 as spring members are alternately stacked in a space between the end surface 12 b of the rotor 12 and the end surface 13 a facing the casing 13.

  As shown in FIG. 1, in the stator 11, a protruding half of a pin (rotating shaft) 25 fitted in the shaft hole 12c of the rotor 12 is inserted into the shaft hole 11c, and the positioning pin 26 is inserted into the positioning groove 11d. Is inserted slidably, the end surface 11b is brought into close contact with the end surface 12a of the rotor 12 against the spring force of the disc spring 18 and is fitted and accommodated in the casing 13, and the annular end plate 19 cannot deviate from the casing 13. And it is fixed so that it cannot rotate. The stator 11 is inserted in a liquid-tight manner in the casing 13 by an O-ring 29. A pressing means 14 is formed by the one-way valves 16 and 17 and the disc spring 18.

The operation will be described below with reference to FIGS. Note that the flow control valve 10 is applied to a compressed fluid circuit, for example, a high pressure hydraulic circuit, the opening 21A is an inlet for compressed fluid (hereinafter referred to as “pressure oil”), and the opening 22A is an outlet for pressure oil. . 5 and 6 show the flow rate control valve 10 shown in FIG. 1 corresponding to the opening 21a of the first flow path 21 and the second flow path 22 of the stator 11 on the contact surface between the stator 11 and the rotor 12. The state of 21b, openings 22a and 22b, and the corresponding two communication grooves 23 and communication grooves 24 of the rotor 12 is viewed from the end surface 12a side of the rotor 12. In FIGS. 5 and 6 , the openings 21a, 21b, 22a, and 22b of the end surface 11b of the stator 11 are drawn with solid lines for easy understanding.

  As shown in FIG. 5, in a state where the positioning pin 26 of the rotor 12 is locked to one end portion of the positioning groove 11d of the stator 11 (hereinafter referred to as “first control position”), the communication groove 23 and 24 are connected only to the openings 21a and 22b, respectively, and are not connected to the openings 22a and 21b. Therefore, the flow control valve 10 is in a state where the first flow path 21 and the second flow path 22 are blocked, that is, in a closed state.

  When the rotor 12 rotates in the clockwise direction indicated by the arrow C in the drawing, each side (end surfaces 23a, 24a side) of the communication grooves 23, 24 gradually communicates with the openings 22a, 21b, respectively (FIG. 7). reference). Thereby, the flow control valve 10 is gradually opened, and the pressure oil starts to flow from the opening 21a to the opening 22a and from the opening 21b to the opening 22b. That is, the pressure oil starts to flow from the first flow path 21 to the second flow path 22 through the first communication groove 23 and the second communication groove 24.

  The rotor 12 further rotates clockwise C, and the positioning pin 26 is locked to the other end of the positioning groove 11d of the stator 11 (hereinafter referred to as “second control position”) as shown in FIG. Then, each one side of the communication groove 23 and the communication groove 24 is fully opened and communicates with the opening 22a and the opening 21b, respectively. Moreover, the other side (end surface 23b, 24b side) of the communication grooves 23 and 24 is connected to the openings 21a and 22b. Thereby, each of the two openings 21a and 21b of the first channel 21 and the second channel 22, the corresponding openings 21a and 22a on each side of the openings 22a and 22b, and the correspondence on each other side The opening portions 21b and 22b to be communicated with each other, and the first channel 21 and the second channel 22 are communicated. Thereby, the flow control valve 10 is fully opened.

  As described above, the first and second flow paths 21 and 22 of the stator 11 are symmetrically disposed on the left and right sides of the straight line α passing through the center O (see FIGS. 2 and 3), and each of these two openings 21a and 21b and openings 22a and 22b are arranged at symmetrical positions on the same circumference, and the communication groove 23 and the communication groove 24 of the rotor 12 are also arranged on the same circumference and have the same shape. . The communication groove 23 and the communication groove 24 correspond to the corresponding openings 21a and 22a on each side of the two openings of the first flow path 21 and the second flow path 22 and on the other side. The openings 21b and 22b are in communication.

  As a result, as shown in FIG. 6, the pressure oil flowing in from the opening 21A of the first flow path 21 branches inside the stator 11 and passes from the opening 21a to the opening 22a through the communication groove 23 to the opening 21b. Then, the air flows from the first through the communication groove 24 to the opening 22b, joins again inside the stator 11, and flows out from the opening 22A of the second flow path 22. As a result, the pressure oil flowing in the communication groove 23 and the communication passage 24 generates the flow forces FH and FH having the same size and flows in the opposite direction. As a result, the flow forces FH and FH due to the pressure oil flowing through the communication groove 23 and the communication groove 24 are canceled out. Thereby, the control force of the rotation of the rotor 12 is not an important factor for the flow force.

  As described above, in order to effectively cancel the two flow forces FH and FH, the openings 21A and 22A, the openings 21a, 21b, 22a and 22b of the first and second flow paths 22 of the stator 11 are provided. In particular, the groove structure dimensions, symmetry, and positioning of the communication grooves 23 and 24 of the rotor 12 are important factors, but these processes are easier than the spool processes and management described above.

  Further, between the contact surfaces of the end surface 11 b of the stator 11 and the end surface 12 a of the rotor 12, the contact state is maintained or maintained only by some external pressure against the fluid pressure applied to the communication grooves 23 and 24 of the rotor 12. Must be. In a state where no fluid pressure is applied, the end surface 12 a of the rotor 12 is held in close contact with the end surface 11 b of the stator 11 only by the spring force of the disc spring 18.

  However, when pressure oil is applied with the first channel 21 as the inlet for pressure oil and the second channel 22 as the outlet for pressure oil, the valve closing state shown in FIG. 5, that is, the openings 22 a and 21 b are Even in the shut-off state, a part of the pressure oil flowing into the communication groove 23 from the opening 21a of the first flow path 21 passes between the rotor 12 and the casing 13 through the one-way valve 16 shown in FIG. It flows into the space between them and acts as a back pressure (back pressure) BP, and in cooperation with the disc spring 18, the rotor 12 is pressed to press the end surface 12 a against the opposing end surface 11 b of the stator 11.

  In addition, the pressure oil that has flowed into the space between the rotor 12 and the casing 13 through the one-way valve 16 from the communication groove 23 that communicates with the first flow path 21 in the valve-closed state is communicated with the communication groove 24 by the one-way valve 17. Outflow to the side is prevented. That is, the flow of the pressure oil to the second flow path 22 side on the fluid outlet side is prevented. Thereby, the fall of the back pressure BP given to the rotor 12 is prevented and the said equilibrium state is hold | maintained.

  Maintaining the equilibrium state means that the area perpendicular to the rotation axis (pin 25) of the pressure oil flow path (communication grooves 23, 24) on the end surface 12a side of the rotor 12 and the end surface 12b side (disc spring 18 side) are maintained. A state (contact state) in which the rotor 12 is compacted to the stator 11 is created by a force corresponding to the product of the difference between the area perpendicular to the rotation axis and the pressure oil pressure. And this oil pressure state can prevent leakage of pressure oil from the contact surface between the end surface 11b of the stator 11 and the end surface 12a of the rotor 12.

  Further, the force required for rotation control of the mechanical external pressure mechanism that maintains the contact state with the pressure of the pressure oil itself using the back pressure (back pressure) BP by pressure oil is the spring force of the disc spring 18 ( The frictional force generated by the reaction force) and the frictional force on the contact surface. The close contact surfaces have surfaces that have been subjected to precise surface processing, and since the liquid film (oil film) is held, smooth sliding occurs. That is, the rotor 12 can be smoothly rotated.

  When the back pressure BP is not used, a necessary pressing force must be generated by the disc spring 18 or the spring. Therefore, the spring force at the time of assembly and the contact generated between the spring and the like after the assembly and the casing 13 are required. The frictional force increases, and the rotation control force must be increased. However, as described above, such a problem can be easily solved by effectively using the back pressure BP.

As a result, the rotating shaft 15 of the rotor 12 can be driven accurately and without being overloaded by the electric motor, and the flow control valve can be electrified. Furthermore, it can be driven only by electric operation without using power assist such as hydraulic pressure or pneumatic pressure, and can easily cope with a compressed fluid circuit (hydraulic circuit) having a high pressure and a large flow rate.
Contrary to the above, the same applies to the case where the second flow path 22 is a fluid inlet and the first flow path 21 is a fluid outlet. At this time, a fluid is introduced into the space between the rotor 12 and the casing 13 from the one-way valve 17 to create a back pressure BP, and the one-way valve 16 is introduced between the rotor 12 and the casing 13. The back pressure BP is held so that the fluid does not flow out from the outlet side. Thereby, the flow control valve 10 can cope with both directions.

  FIG. 9 shows a change in the passage area of the fluid of the flow control valve 10 shown in FIGS. 5 and 6 in a systematic circuit. In FIG. 9, in the flow path between the openings 21a and 22a, the flow area on the outlet side is controlled when viewed from the communication groove 23. In the flow path between the openings 21b and 22b, the flow path is viewed from the communication groove 24. It becomes the control system body of the flow path area on the inlet side. In FIG. 9, the fluid flow indicated by the solid arrow indicates the case where the first flow path 21 is the fluid inlet side and the second flow path 22 is the outlet side, and the fluid flow indicated by the dotted arrow is The case where the second channel 22 is the fluid inlet side and the first channel 21 is the outlet side is shown.

  The flow control valve that can handle both directions has been described above. However, if the flow control valve is compatible with one direction, the one-way valve may be provided only in one of the communication grooves. That is, in FIG. 5, when the first flow path 21 is the fluid inlet side and the second flow path 22 is the outlet side, it communicates with one opening 21a on the inlet side that communicates when the valve is closed. If the one-way valve 16 is provided only on the communication groove 23 side, and the second channel 22 is the fluid inlet side and the first channel 21 is the outlet side, on the contrary, The one-way valve 17 is provided only on the side of the communication groove 24 that communicates with the one opening 22b on the inlet side that communicates.

  In this case, a channel for introducing a part of the fluid to the end face 12b side, for example, a small hole, may be provided instead of the one-way valve. Thus, it is possible to aim at the reduction of a number of parts, the improvement of the assembly | attachment accompanying this, and the cost reduction by making it a small hole instead of a one-way valve. 10 and 11 show a systematic circuit in the case of a small hole. In addition, the flow paths 31 and 32 shown in FIG. 10, FIG. 11 have each shown the said small hole.

  Moreover, in the said embodiment, although the initial load for maintaining the close_contact | adherence state with the stator 11 of the rotor 12 is produced with springs, such as a disc spring 18, etc., a spring part, a rotor, and a rotating shaft are made into one body, A spring part A plurality of slits may be cut in a portion corresponding to the above, and a type of flexible coupling in which a portion sandwiched between these slits is provided with a spring property may be used. An example of such a flexible coupling is Flexus (registered trademark). And by setting it as such a structure, it becomes possible to make a parallelism more stable in connection with rotation of the stator side (fixed) and rotor side (rotation side) after a reduction of a number of parts and assembly and assembly. .

  Further, unlike the needle valve system, electrical control is facilitated, so that the position (distance) of the control unit and the operation unit of the flow rate control system can be separated. In other words, the piping of the hydraulic circuit up to the operating unit is not required as in the prior art, and it becomes possible to incorporate a flow control valve into a part of the main circuit, and the piping associated with the reduction in the number of piping and the shortening of the long fluid passage This leads to a reduction in noise generated from the fluid inside and a reduction in turbulence. Also, by adapting the housing and stator (fixed side), it is possible to diversify with direct piping and manifolds.

Furthermore, the positional relationship between the stator side and the rotor side, that is, the control range may be specified by mechanically positioning the operating range between them. Further, position control related to electric control can be performed by using an electric displacement detection sensor such as a potentiometer or an encoder in conjunction with the rotation shaft of the rotor.
In addition, the control of the rotating shaft of the rotor uses an electric motor, whether directly or indirectly, and a reduction mechanism such as a gear must be used during that time. Is not what you need.

In the flow control valve 10 described above, the increase in the control force generated from the flow force (generated fluid force) in the fluid and the control fluid pressure in the control of the high pressure and the large flow rate is reduced by the operation to the back pressure of the fluid pressure. By doing so, it becomes possible to support hydraulic test stands and flight technology systems where high pressure is being promoted .

DESCRIPTION OF SYMBOLS 1 Body 2 Needle valve 2a Valve shaft 2b Thread part 2c Tip part 2d Tapered surface 3 Valve seat 4 Handle 10 Flow control valve 11 Stator (Valve body, fixed part)
11a End surface on one side 11b End surface on the other side 11c Shaft hole 11d Groove for positioning 12 Rotor (valve element, rotating part)
12a End surface on one side 12b End surface on the other side 12c Shaft hole 13 Casing 13a End surface 13b Shaft hole 14 Pressing means 15 Rotating shaft 16, 17 One-way valve 18 Belleville spring 19 End plate 21 First flow path 21A Openings 21a, 21b Opening 22 Second flow path 22A Opening 22a, 22b Opening 23, 24 Communication groove 23a, 23b, 24a, 24b End 25 Pin (rotating shaft)
26 Positioning pin 27, 28, 29 O-ring 31, 32 Flow path (small hole)
FH Flow Force BP Back Pressure (Back pressure )

Claims (4)

The first flow path and the second flow path are provided so as to penetrate from one end face to the other end face, and these first flow path and second flow path are on both sides of a straight line passing through the center. A stator that is symmetrically arranged and has one opening on the one end face, and is bifurcated inside to form two openings on the other end face;
One end face is in close contact with the other end face of the stator and is rotatable, and the first flow path and the second flow path are blocked at the first control position on the one end face. As the first control position is rotated from the first control position to the second control position, the corresponding openings on the one side of the two openings of the first flow path and the second flow path A rotor provided with a first communication groove and a second communication groove for communicating the corresponding openings on the other side with the first flow path and the second flow path;
A casing for housing the stator and the rotor;
A flow control valve, comprising: a pressing means provided between an end face on the other side of the rotor and a casing and causing the end face on one side of the rotor to be in close contact with the end face on the other side of the stator. Each of the two openings of the first and second flow paths opening on the other end face of the stator is disposed on the same circumference,
The first and second communication grooves of the rotor are characterized in that at least both ends are arranged on the same circumference facing the two openings of the first and second flow paths. The flow control valve according to claim 1. The pressing means includes a spring contracted between an end face on the other side of the rotor and an end face facing the casing;
Provided in the rotor, each one end is opened to the bottom surface of each of the first and second communication grooves, and each other end is opened to the other end surface, so that each communication groove side to the other end surface side The flow control valve according to claim 1 or 2, comprising a one-way valve that allows a flow of fluid only to the head. The pressing means includes a spring contracted between an end face on the other side of the rotor and an end face facing the casing;
When one of the first flow path and the second flow path of the stator is used as a fluid inlet, and the other is used as a fluid outlet, the communication groove on the side where the fluid can be introduced to the communication groove when the valve is closed. The flow rate control according to claim 1 or 2, comprising a flow path for supplying a part of fluid by opening one end on the bottom surface and opening the other end on the other end surface of the rotor. valve.

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