JP3925207B2 - Flow control valve - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a flow rate control valve that controls the flow rate of a fluid such as air, and more particularly to a flow rate control valve that controls in proportion to the output of an electromagnetic actuation mechanism.
[0002]
[Prior art]
A flow control valve that controls proportionally with respect to the output of an electromagnetic operation mechanism generally operates a spool that is slidably disposed in a sleeve to a position where the suction force of the electromagnetic solenoid and the reaction force of the spring are balanced. A spool valve is used.
The spool valve is configured so that the spool slides along the inner peripheral surface of the sleeve having a port formed on the side surface.
In addition, it is necessary to provide a clearance between them, and a seal such as rubber cannot be used, so that a complete seal is impossible. In order to improve the sealing performance between the sleeve and the spool, it is necessary to minimize the clearance between the two and ensure the sliding performance. However, in order to satisfy such a requirement, high-precision processing is required, which increases processing costs. Also, the spool valve malfunctions when dust or the like bites between the sleeve and the spool. In order to solve such a problem of the spool valve type flow control valve, the present applicant has proposed a poppet type flow control valve as Japanese Patent Application Laid-Open No. 2000-55211.
[0003]
[Problems to be solved by the invention]
The flow control valve proposed in the above Japanese Patent Laid-Open No. 2000-55211 is a two-way valve type flow control valve and needs to be used in combination with another valve for switching between supply and exhaust. There is a problem that the number of times of operation of another combined valve becomes very large.
[0004]
The present invention has been made in view of the above-mentioned facts, and the main technical problem thereof is a three-way valve type flow rate that can be controlled proportionally with respect to the output of the electromagnetic actuation mechanism using a poppet valve mechanism with good sealing performance. It is to provide a control valve.
[0005]
[Means for Solving the Problems]
According to the present invention, in order to solve the above main technical problem, “a valve body including an input port, an output port, and a discharge port, and a valve that is disposed in the valve body and controls communication between the ports. Mechanism, Equipped with electromagnetic coil unit A flow control valve having an electromagnetic actuation mechanism for driving the valve mechanism,
The valve body is provided with a communication chamber communicating the input port and the output port, and two valve holes formed opposite to each other on both sides of the communication chamber, and an annular partition plate is provided in the communication chamber. Arranged,
The valve mechanism is seated on a sliding portion provided at one end portion and slidably fitted in one of the valve holes, and a seating portion provided at a central portion and formed on an inner periphery of the annular partition plate. A first valve portion comprising a tapered surface, a second valve portion provided at the other end, and a communication passage provided in the axial direction and communicating with the discharge port. The disc,
A sliding portion that is slidably fitted to the other of the valve holes, a valve portion that is provided at one end portion and abuts against the second valve portion of the first valve body, and is provided penetrating in the axial direction. A second valve body having a communication passage that communicates with the discharge port;
Between the sliding portion of the first valve body and the inner peripheral surface of the one valve hole Disposed first seal When,
Between the sliding portion of the second valve body and the inner peripheral surface of the other valve hole Disposed second seal When,
Disposed between the valve body and the first valve body inside the one valve hole; A first spring that biases the first valve body in a direction in which the first valve portion is seated on the seat portion of the partition plate;
A second spring that urges both the first valve body and the second valve body in a direction to separate them, and
Sliding surface diameters of the first seal and the second seal, a diameter of a contact portion seated on the seating portion of the partition plate in the first valve portion of the first valve body, The diameter of the contact portion where the valve portion of the second valve body and the second valve portion of the first valve body abut is set equal,
The electromagnetic actuation mechanism is When a voltage is applied to the electromagnetic coil unit The second valve element on the first valve element side Move A flow control valve ”is provided which is configured as described above.
[0006]
DETAILED DESCRIPTION OF THE INVENTION
DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, a preferred embodiment of a flow control valve configured according to the invention will be described with reference to the accompanying drawings.
[0007]
FIG. 1 shows a first embodiment of a flow control valve constructed according to the present invention.
The flow control valve 2 in the illustrated embodiment includes a valve body 3, a valve mechanism 4 disposed in the valve body 3, and an electromagnetic operation mechanism 5 that drives the valve mechanism 4. The valve body 3 is composed of two body pieces 3a and 3b in the illustrated embodiment. In this way, the input port 31, the output port 32, and the discharge port 33 are formed in the valve body 3 including the two body pieces 3a and 3b. A communication chamber 34 that communicates the input port 31 and the output port 32 is formed at the center of the valve body 3. Further, the valve body 3 is provided with two valve holes 35a and 35b formed on both sides of the communication chamber 34 so as to face each other. One valve hole 35 a is provided at the center of one body piece 3 a and opens to the communication chamber 34 and communicates with the discharge port 33. The other valve hole 35b is provided in the center of the other body piece 3b on the same axis as the valve hole 35a, and opens to the communication chamber 34. An annular partition plate 36 is disposed in the communication chamber 34 formed in the valve body 3 including the two body pieces 3a and 3b, and the communication chamber 34 is formed by the partition plate 36 and a valve mechanism 4 described later. It is divided into an input side chamber 34a and an output side chamber 34b.
[0008]
The valve mechanism 4 disposed in the valve body 3 is slidably disposed in the first valve body 41 slidably disposed in the one valve hole 35a and in the other valve hole 35b. A second valve body 42 is provided. The first valve body 41 is provided at one end portion and is slidably fitted into the valve hole 35a, between the central small diameter portion 412, and between the sliding portion 411 and the central small diameter portion 412. A first valve portion 413 having a tapered surface seated on a seat portion 361 formed on the inner periphery of the partition plate 36 and a second valve portion 414 provided at the other end portion are provided. In addition, the outer diameter (D1) of the sliding part 411 which comprises the 1st valve body 41, and the outer diameter (D2) of the 2nd valve part 414 are formed in the same diameter. The first valve body 41 has a communication passage 415 penetrating in the axial direction. Formed, The communication passage 415 communicates with the discharge port 33 through a first pressure chamber 37 formed between one end of the first valve body 41, that is, the left end in FIG. 1 and the body piece 3a. Thus, the first pressure chamber 37 forms part of the one valve hole 35a. A first seal 43 slidably contacting the outer peripheral surface of the sliding portion 411 is attached to a part of the inner peripheral surface of the valve hole 35a formed in the body piece 3a. The first seal 43 partitions the input side chamber 34a of the communication chamber 34, that is, the input port 31, and the first pressure chamber 37, that is, the discharge port 33.
[0009]
The second valve body 42 slidably disposed in the valve hole 35b is opposed to the sliding portion 421 slidably fitted in the valve hole 35b and one end, that is, the first valve body 41. The valve part 422 provided in the edge part by the side of this and formed in larger diameter than the sliding part 421 is provided. The valve portion 422 constituting the second valve body 42 is formed at an end portion facing the second valve portion 414 of the first valve body 41, and a taper with which the outer peripheral edge of the second valve portion 414 contacts. A seating portion 422a having an inner peripheral surface is provided. In addition, a communication groove 422b formed so as to penetrate in the axial direction is provided around the valve portion 422.
. A communication passage 423 that penetrates in the axial direction is formed in the second valve body 42. The communication passage 423 communicates with the discharge port 33 through the communication passage 415 formed in the first valve body 41 and the first pressure chamber 37, and the other end side of the second valve body 42, that is, the figure. 1 communicates with the second pressure chamber 38 formed on the right side. Therefore, the first pressure chamber 37 and the second pressure chamber 38 communicate with each other in the first valve body 41. 415 and the second valve body 42 communicate with each other through a communication passage 423. Note that a second seal 44 slidably contacting the outer peripheral surface of the sliding portion 411 is attached to a part of the inner peripheral surface of the valve hole 35b formed in the body piece 3b. The second seal 44 partitions the output side chamber 34 b of the communication chamber 34, that is, the output force port 32, and the second pressure chamber 38, that is, the discharge port 33. In the illustrated embodiment, the second valve portion 414 of the first valve body 41 and the valve portion 422 of the second valve body 42 are seated on the valve portion 422 of the second valve body 42. Although the example provided with the part 422a was shown, you may provide a seating part in the 2nd valve part 414 of the 1st valve body 41. FIG.
[0010]
In the illustrated embodiment, the sliding surface diameter that is in sliding contact with the first seal 43 and the second seal 44, that is, the outer diameter (D1) of the sliding portion 411 of the first valve body 41 and the second valve. The outer diameter (D3) of the sliding part 421 of the body 42 and the diameter of the contact part seated on the seating part 361 of the partition plate 36 in the first valve part 413 comprising the tapered surface of the first valve part 413 (D4) (diameter of the seating portion 361 of the partition plate 36), the outer peripheral edge of the second valve portion 414 of the first valve body 41 in the seating portion 422a composed of the tapered inner peripheral surface of the second valve body 42 The diameter (D5) of the abutting portion that abuts (the outer diameter (D2) of the second valve portion 414) is all configured to be equal. In the illustrated embodiment, since the first seal 43 and the second seal 44 are attached to the valve body 3, the sliding surface diameter that is in sliding contact with the seal is that of the sliding portion 411 of the first valve body 41. The outer diameter (D1) and the outer diameter (D3) of the sliding portion 421 of the second valve body 42 are the same as the first seal body 43 and the second valve 44. When mounted on the body 42, the sliding surface diameter that comes into sliding contact with the seal is the outer diameter of the valve hole 35a and the valve hole 35b formed in the valve body 3.
[0011]
The first pressure chamber 37 forming a part of the one valve hole 35a is provided between one end of the first valve body 41 and the valve body (body piece 3a). A first compression coil spring 45 is disposed, and the first compression coil spring 45 moves the first valve body 41 to the right in FIG. 1, that is, the first valve portion of the first valve body 41. 413 is urged in the direction of seating on the seating portion 361 of the partition plate 36. Further, a second compression coil spring 46 is disposed between the first valve body 41 and the second valve body 42, and the second compression coil spring 46 is a direction in which both valve bodies are separated from each other. Is energized. Here, the spring characteristics and the set pressure of the first compression coil spring 45 and the second compression coil spring 46 will be described with reference to FIG. The first compression coil spring 45 has a free length of L1, and when set, the first compression coil spring 45 is compressed and set to the first set position S1, and the set load at this time is F1. The load of the first compression coil spring 45 set in this way changes linearly along the first coil spring load line SL1 from the first set position S1 to the compression end position S0. The second compression coil spring 46 has a free length L2 and is set after being compressed to the second set position S2 at the time of setting. The set load at this time is F2. The second compression coil spring 46 set in this way has a second coil spring load from the second set position S2 to the first set position S1 where the second valve body 42 contacts the first valve body 41. The load changes linearly along the line SL2. The spring load when the second compression coil spring 46 is compressed to the first set position S1, that is, the load at the time of the full stroke of the second compression coil spring 46 is F21. Lower than 45 set load F1. The first coil spring load line SL1 of the first compression coil spring 45 and the second coil spring load line SL2 of the second compression coil spring 46 have the same inclination angle, that is, the spring constant.
[0012]
When the first compression coil spring 45 and the second compression coil spring 46 having the above-described spring constant are arranged as shown in FIG. 1, the first valve portion 413 of the first valve body 41 is the first valve portion 413. Of the compression coil spring 45 is seated on the seating portion 361 of the partition plate 36, and the right end of the valve portion 422 constituting the second valve body 42 is located on the left end side of the valve hole 35b of the body piece 3b. It is made to contact | abut to the formed step part 301b. Therefore, there is a gap between the seating portion 422a formed of a tapered inner peripheral surface constituting the valve seat portion 422 of the second valve body 42 and the outer peripheral edge of the second valve portion 414 constituting the first valve body 41. In the set state, a gap is formed as shown in FIG.
[0013]
Next, the electromagnetic actuation mechanism 5 that drives the valve mechanism 4 described above will be described.
The electromagnetic actuation mechanism 5 in the illustrated embodiment includes a case piece 51 mounted on the right end in the figure of the body piece 3b constituting the valve body 3, an electromagnetic coil unit 52 disposed in the case piece 51, A fixed yoke 53 that forms a magnetic path generated by the electromagnetic coil unit 52, a movable yoke 54 that is attracted by the magnetic force generated in the fixed yoke 53 in the electromagnetic coil unit 52, and an operating rod 55 that is connected to the movable yoke 54. It is equipped with. The electromagnetic coil unit 52 includes an annular bobbin 521 formed of an appropriate synthetic resin, a coil 522 wound around the bobbin 521, and a lead wire 523 that supplies power to the first coil 522.
[0014]
The fixed yoke 53 is formed of a magnetic material, and includes a cylindrical portion 531 and an annular portion 532 formed radially at an axial intermediate portion of the cylindrical portion 531, and the annular portion 532 is a body piece. 3b and the electromagnetic coil unit 52. Further, the cylindrical portion 531 constituting the fixed yoke 53 is fitted to a fitting hole 302b formed in the body piece 3b on the left side of the annular portion 532 in the drawing, and the right portion in the drawing from the annular portion 532 on the drawing. The electromagnetic coil unit 52 is fitted into the center hole 521a of the annular bobbin 521. The cylindrical portion 531 constituting the fixed yoke 53 is formed with an insertion hole 531a penetrating in the axial direction in the central portion, and a plurality of communication holes penetrating in the axial direction outward in the radial direction of the insertion hole 531a. 531b is formed. A seal 533 is attached to the outer periphery of the left portion in the drawing from the annular portion 532 of the cylindrical portion 531 constituting the fixed yoke 53, and seals between the inner peripheral surface of the fitting hole 302b of the body piece 3b. ing. Further, a seal 534 is attached to the outer periphery of the portion on the right side of the annular portion 532 of the cylindrical portion 531 constituting the fixed yoke 53 in the drawing to seal between the inner peripheral surface of the central hole 521a of the annular bobbin 521. ing.
[0015]
The movable yoke 54 is formed of a magnetic material, and is disposed on the right side of the fixed yoke 53 in FIG. The movable yoke 54 is formed with a fitting hole 54a penetrating in the axial direction at the center, and a communicating hole 54b penetrating in the axial direction is formed radially outward of the fitting hole 54a. . The operating rod 55 is made of a nonmagnetic material such as stainless steel, and is inserted through an insertion hole 531a formed at the center of the cylindrical portion 531 constituting the fixed yoke 53. It is slidably supported in the axial direction by a bush 535 mounted on the inner peripheral surface of 531a. The actuating rod 55 is configured so that the right end portion thereof in FIG. 1 is fitted into the fitting hole 54a of the movable yoke 54 and operates integrally with the movable yoke 54 in the axial direction. The left end, that is, the tip of the operating rod 55 in FIG. 1 is configured to contact the right end of the second valve body 42 in FIG.
[0016]
A support member 56 for supporting the right end portion, that is, the rear end portion of the operating rod 55 in FIG. The support member 56 has a cylindrical portion 561 and a bottom portion 562 provided at the right end of the cylindrical portion 561 in FIG. 1, and the left end portion of the cylindrical portion 561 in FIG. The bobbin 521 is fitted in the central hole 521a, and the bottom portion 562 is disposed in contact with the bottom portion 511 of the casing 51. A step portion 561a is provided on the right outer periphery of the fitting portion of the cylindrical portion 561 of the support member 56 with the bobbin 521 in FIG. 1, and the bobbin 521 is positioned by contacting the step portion 561a and the bobbin 521. Yes. An annular clamping member 57 is fitted to the step portion 561a, and the coil unit 52 is sandwiched between the annular portion 532 constituting the fixed yoke 53. A seal 563 is attached to the outer periphery of the fitting portion with the bobbin 521 in the cylindrical portion 561 constituting the support member 56, and seals between the inner peripheral surface of the central hole 521a of the annular bobbin 521.
[0017]
A support ring 58 is disposed in the support member 56, and a bush 59 is fitted on the inner periphery of the support ring 58. The bush 59 supports the rear end portion of the operating rod 55 so as to be slidable in the axial direction. In addition
The support ring 58 is formed with a communication hole 581 penetrating in the axial direction. A third pressure chamber 60 is formed at the rear end side of the operating rod 55, that is, between the support ring 58 and the bush 59 and the bottom portion 562 of the support member 56. The third pressure chamber 60 is communicated with the working chamber 61 of the movable yoke 54 through a communication hole 581 provided in the support ring 58. Therefore, the second pressure chamber 38 and the third pressure chamber 60 include a communication hole 531 b formed in the cylindrical portion constituting the fixed yoke 53, a communication hole 54 b formed in the movable yoke 54, and the working chamber 61. And communicated with each other through a communication hole 581 formed in the support ring 58. The second pressure chamber 38 and the first pressure chamber 37 communicate with each other through a communication passage 423 formed in the second valve body 42 and a communication passage 415 formed in the first valve body 41. Therefore, the first pressure chamber 37, the second pressure chamber 38, and the third pressure chamber 60 are in communication with each other.
[0018]
The flow control valve 2 in the first embodiment is configured as described above, and the operation thereof will be described below with reference to FIGS. 3 and 4. FIG. 1 shows a state in which no voltage is applied to the coil 522 of the electromagnetic coil unit 52 constituting the electromagnetic operating mechanism 5. In this state, as described above, the first valve portion 413 of the first valve body 41 is seated on the seat portion 361 of the partition plate 36, and the seat portion 422 a of the second valve body 42 and the first valve body 41. A gap is formed between the outer periphery of the second valve portion 414 constituting the. Accordingly, the communication between the input port 31 and the output port 32 is blocked, and the output port 32 is connected to the output side chamber 34b of the communication chamber 34, the second port. Seating part of valve body 42 It communicates with the discharge port 33 through a gap between 422a and the second valve portion 414 constituting the first valve body 41, a communication passage 415 formed in the first valve body 41, and the first pressure chamber 37. As a result, an actuator chamber (not shown) connected to the output port 32 by a pipe (not shown) communicates with the discharge port 33, so that the actuator is maintained in an inoperative state.
[0019]
Here, the pressure balance of the 1st valve body 41 in the state shown in FIG. 1 is demonstrated.
Although the pressure of the input port 31 acts on the first valve body 41, the outer diameter (D1) of the sliding portion 411 of the first valve body 41, which is the sliding surface diameter that is in sliding contact with the first seal 43, Since the diameter (D4) of the contact portion of the first valve portion 413 with the partition plate 36 in the first valve portion 413 is equal, the first valve body 41 generates a thrust due to the pressure of the input port 31. do not do.
Further, the pressure of the output port 32 acts on the first valve body 41, but the outer peripheral edge of the second valve portion 414 of the first valve body 41 in the seating portion 422 a of the second valve body 42 abuts. The diameter (D5) of the contact part (the outer diameter (D2) of the second valve part 414) and the diameter of the contact part of the first valve part 413 of the first valve part 413 with the partition plate 36 (D4) ) Is equal, no thrust is generated in the first valve body 41 due to the pressure of the output port 32. Furthermore, although the pressure of the discharge port 33 acts on the first valve body 41, the outer diameter (D1) of the sliding portion 411 is equal to the diameter (D4) of the abutting portion. No thrust is generated in 41 due to the pressure of the discharge port 33.
[0020]
Next, the pressure balance of the second valve body 42 in the state shown in FIG. 1 will be described.
The pressure of the output port 32 acts on the second valve body 42, but the contact of the outer peripheral edge of the second valve portion 414 of the first valve body 41 in the seating portion 422 a of the second valve body 42 abuts. The diameter (D5) of the portion and the outer diameter (D3) of the sliding portion 421 of the second valve body 42, which is the sliding surface diameter that is in sliding contact with the second seal 44, are equal. No thrust is generated by the pressure of the output port 32.
Further, although the pressure of the discharge port 33 acts on the second valve body 42, since the diameter (D5) of the contact portion and the outer diameter (D3) of the sliding portion 421 are equal, No thrust is generated in the body 42 due to the pressure of the discharge port 33.
For this reason, only the force of the electromagnetic operating mechanism 5 and the second compression coil spring 46 acts on the second valve body 42. Therefore, the second valve body 42 stops at a balance point between the driving force of the electromagnetic actuating mechanism 5 and the reaction force of the second compression coil spring 46.
[0021]
When a voltage is applied to the coil 522 of the electromagnetic coil unit 52 from the state of FIG. 1, a magnetic path is formed through the fixed yoke 53, and the movable yoke 54 is attracted to the fixed yoke 53 and moved to the left in FIG. . As the movable yoke 54 moves, the operating rod 55 moves to the left, and the second valve element 42 moves to the left against the spring force of the second compression coil spring 46. As a result, the seating surface 422a of the second valve body 42 comes into contact with the outer peripheral edge of the second valve portion 414 constituting the first valve body 41, and further, as shown in FIG. The first valve element 41 is moved to the left against the spring force. Accordingly, the first valve portion 413 of the first valve body 41 opens away from the seating portion 361 of the partition plate 36, and the fluid supplied to the input port 31 is supplied to the input side chamber 34a and the output side chamber 34b of the communication chamber 34. To the actuator (not shown) from the output port 32.
[0022]
By the way, as described above, the outer diameter (D1) of the sliding portion 411 of the first valve body 41, which is the sliding surface diameter that is in sliding contact with the first seal 43 and the second seal 44 constituting the valve mechanism 4, and The outer diameter (D3) of the sliding portion 421 of the second valve body 42 and the contact with which the first valve portion 413 having the tapered surface of the first valve portion 413 is seated on the seating portion 361 of the partition plate 36. Part diameter (D4) (diameter of the seating part 361 of the partition plate 36) and the second valve part 414 of the first valve body 41 in the seating part 422a composed of the tapered inner peripheral surface of the second valve body 42. Since the diameter (D5) of the abutting portion with which the outer peripheral edge of the second abutting portion (the outer diameter (D2) of the second valve portion 414) is all equal, the first valve body 41 and the second valve body 42 are configured. No thrust is generated by fluid pressure. Therefore, only the force of the first compression coil spring 45 acting on the second valve body 42 via the electromagnetic operating mechanism 5 and the first valve body 41 acts. Accordingly, the second valve body 42 and the first valve body 41 are integrated, and the seating surface 422a of the second valve body 42 contacts the outer peripheral edge of the second valve portion 414 constituting the first valve body 41. In this state, the electromagnetic actuator 5 stops at a balance point between the driving force of the electromagnetic operating mechanism 5 and the reaction force of the second compression coil spring 46.
[0023]
When the flow control valve 2 is operated as described above to supply the fluid supplied to the input port 31 to the actuator (not shown) from the output port 32 and drive the actuator, and then the actuator is to be stopped at a predetermined operating position. Will be described.
That is, the voltage applied to the coil 522 of the electromagnetic coil unit 52 is reduced from the state shown in FIG. 3, and the driving force of the electromagnetic actuating mechanism 5, that is, the attractive force of the electromagnetic solenoid, is set to the set load F1 of the first compression coil spring 45. In the following, the range is equal to or greater than the load F21 during the full stroke of the second compression coil spring 46. As a result, the first valve body 41 and the second valve body 42 move to the right in the drawing by the spring force of the first compression coil spring 45, and as shown in FIG. The first valve portion 413 stops at a position where it is seated on the seat portion 361 of the partition plate 36. Accordingly, since the communication between the input port 31 and the output port 32 is blocked, the actuator (not shown) is stopped at a predetermined operating position.
[0024]
Next, when returning an actuator (not shown) to the operation start position, the supply of electric power to the coil 522 of the electromagnetic coil unit 52 is interrupted to deenergize the electromagnetic solenoid. As a result, each member of the flow control valve 2 returns to the state shown in FIG. In the state shown in FIG. 1, as described above, the first valve portion 413 of the first valve body 41 is seated on the seat portion 361 of the partition plate 36, and the seat portion 422 a of the second valve body 42 and the first Since a gap is formed between the second valve portion 414 constituting the valve body 41, the communication between the input port 31 and the output port 32 is blocked, and the output port 32 is connected to the output side chamber 34b of the communication chamber 34, Second Seating part of valve body 42 Because the fluid is communicated with the discharge port 33 through the gap between the second valve portion 414 constituting the first valve body 41, the communication passage 415 formed in the first valve body 41, and the first pressure chamber 37. The working fluid in the working chamber of an actuator (not shown) connected to the output port 32 is discharged from the discharge port 33 and returns to the operation start position.
[0025]
As described above, the flow control valve 2 in the illustrated embodiment controls the input port 31, the output port 32, and the discharge port 33 by the valve mechanism 4 having the first valve body 41 and the second valve body 42. Since it is a way valve, switching between air supply and exhaust can be performed by this single flow control valve. Since it is not necessary to use in combination with another valve for switching between air supply and exhaust, the fluid circuit configuration is simplified. Further, since the valve mechanism 4 having the first valve body 41 and the second valve body 42 is a poppet valve type, the seal is reliable, and even if foreign matter such as dust adheres to the seating portion, Since it can flow, it does not cause malfunction.
[0026]
Next, a second embodiment of the flow control valve according to the present invention will be described with reference to FIG. In addition, in the flow control valve 2a in 2nd Embodiment shown in FIG. 5, the same code | symbol is attached | subjected to the same member as the flow control valve 2 in the said 1st Embodiment, and the description is abbreviate | omitted. .
The difference between the flow control valve 2 in the first embodiment and the flow control valve 2 a in the second embodiment is that the flow control valve 2 in the first embodiment has a first pressure chamber 37 and a discharge port 33. In contrast, the flow rate control valve 2a in the second embodiment is in communication with the second pressure chamber 38 and the discharge port 33. As described above, the first pressure chamber 37 and the second pressure chamber 38 communicate with each other through the communication passage 415 formed in the first valve body 41 and the communication passage 423 formed in the second valve body 42. Therefore, the functions are substantially the same, and the flow rate control valve 2a in the second embodiment also has the same effect as the flow rate control valve 2 in the first embodiment.
[0027]
Next, a third embodiment of the flow control valve according to the present invention will be described with reference to FIG. In the flow control valve 2b in the third embodiment shown in FIG. 6, the same members as those of the flow control valve 2 in the first embodiment and the flow control valve 2a in the second embodiment are the same. A reference numeral is attached and the description thereof is omitted. The flow control valve 2b in the third embodiment is characterized in that the second valve body 42 of the valve mechanism 4 is operated by a pull-type electromagnetic operation mechanism 5b. That is, when a voltage is applied to the electromagnetic coil unit of the electromagnetic actuation mechanism 5b, a tensile force is applied to the second valve body to move it to the first valve body side. In the illustrated flow control valve 2b, the electromagnetic actuating mechanism 5b is arranged on the left side of the valve mechanism 4 in the figure. The actuating rod 55 constituting the electromagnetic actuating mechanism 5b is disposed through the communication passage 415 formed in the first valve body 41 and the communication passage 423 formed in the second valve body 42. The tip (right end in FIG. 6) is connected to the second valve element 42 by caulking. The flow rate control valve 2b in the third embodiment configured as described above includes an electromagnetic operating mechanism 5b. Apply voltage to the electromagnetic coil unit Then, the actuating rod 55 is actuated to the left in FIG. 6 to move the second valve element 42 to the left against the spring force of the second compression coil spring 46, and the first valve element 41 is moved to the left against the spring force of the first compression coil spring 45. In addition, about the action | operation form of the valve mechanism 4 which consists of the 1st valve body 41 and the 2nd valve body 42, it is the same as that of the flow control valve 2a in the said 1st Embodiment and the flow control valve 2a in 2nd Embodiment. The above-described embodiments have the same operational effects.
[0028]
【The invention's effect】
Since the flow control valve according to the present invention is configured as described above, the following effects can be obtained.
[0029]
That is, the flow control valve according to the present invention is provided between the sliding portion of the first valve body and the inner peripheral surface of the one valve hole, and the sliding portion of the first seal and the second valve body. The sliding surface diameter of the second seal disposed between the inner peripheral surface of the other valve hole and the contact portion seated on the seating portion of the partition plate in the first valve portion of the first valve body Since the diameter and the diameter of the contact portion on which the second valve portion of the first valve body seats in the seating portion of the second valve body are set equal, the first valve body and the second valve Even if the pressure of the working fluid flowing from the input port through the communication chamber to the output port acts on the body, no axial driving force is generated by the fluid pressure. Therefore, the stroke amount (opening area of the valve), that is, the flow rate of the first valve body and the second valve body functions as a proportional valve in which the operation force of the electromagnetic operation mechanism is proportional. Incidentally, the operating force of the electromagnetic operating mechanism may be a pressing force as in the first embodiment, or may be a tensile force as in the third embodiment. The flow control valve according to the present invention is a three-way valve that controls the input port, the output port, and the discharge port by a valve mechanism having a first valve body and a second valve body. Can be performed with this single flow control valve. Since it is not necessary to use in combination with another valve for switching between air supply and exhaust, the fluid circuit configuration is simplified. Further, since the valve mechanism having the first valve body and the second valve body is a poppet valve type, the seal is reliable, and even if foreign matter such as dust adheres to the seating portion, it can be flowed by the working fluid. Because it can, it will not cause malfunction.
[Brief description of the drawings]
FIG. 1 is a sectional view showing a first embodiment of a flow control valve constructed according to the present invention.
FIG. 2 is an explanatory diagram showing spring characteristics of first and second springs constituting the flow control valve shown in FIG. 1;
3 is a cross-sectional view showing a first operating state of the flow control valve shown in FIG.
4 is a cross-sectional view showing a second operating state of the flow control valve shown in FIG.
FIG. 5 is a cross-sectional view showing a second embodiment of a flow control valve configured according to the present invention.
FIG. 6 is a cross-sectional view showing a third embodiment of a flow control valve configured according to the present invention.
[Explanation of symbols]
2: Flow control valve (first embodiment)
2a: Flow control valve (second embodiment)
2b: Flow control valve (third embodiment)
3: Valve body
31: Input port
32: Output port
33: Discharge port
34: Communication room
35a: One valve hole
35b: the other valve hole
36: Partition plate
37: First pressure chamber
38: Second pressure chamber
4: Valve mechanism
41: First valve body
411: sliding part
413: 1st valve part
414: Second valve part
42: Second valve body
421: sliding part
422: Valve part
43: Second seal
44: Second seal
45: First compression coil spring
46: Second compression coil spring
5: Electromagnetic actuation mechanism
51: Caseig
52: Electromagnetic coil unit
521: bobbin
522: Coil
523: Lead wire
53: Fixed yoke
54: Movable yoke
55: Actuating rod
56: Support member
58: Support ring
60: Third pressure chamber

Claims (1)

A valve body having an input port, an output port, and a discharge port; a valve mechanism disposed in the valve body for controlling communication between the ports; and an electromagnetic operating mechanism having an electromagnetic coil unit for driving the valve mechanism. A flow control valve having
The valve body is provided with a communication chamber communicating the input port and the output port, and two valve holes formed opposite to each other on both sides of the communication chamber, and an annular partition plate is provided in the communication chamber. Arranged,
The valve mechanism is seated on a sliding portion provided at one end portion and slidably fitted in one of the valve holes, and a seating portion provided at a central portion and formed on an inner periphery of the annular partition plate. A first valve portion comprising a tapered surface, a second valve portion provided at the other end, and a communication passage provided in the axial direction and communicating with the discharge port. The disc,
A sliding portion that is slidably fitted to the other of the valve holes, a valve portion that is provided at one end portion and abuts against the second valve portion of the first valve body, and is provided penetrating in the axial direction. A second valve body having a communication passage that communicates with the discharge port;
A first seal disposed between the sliding portion of the first valve body and the inner peripheral surface of the one valve hole;
A second seal disposed between the sliding portion of the second valve body and the inner peripheral surface of the other valve hole;
The valve body is disposed between the valve body and the first valve body within the one valve hole, and the first valve body is seated on the seat portion of the partition plate. A first spring biasing in the direction;
A second spring that urges both the first valve body and the second valve body in a direction to separate them, and
Sliding surface diameters of the first seal and the second seal, a diameter of a contact portion seated on the seating portion of the partition plate in the first valve portion of the first valve body, The diameter of the contact portion where the valve portion of the second valve body and the second valve portion of the first valve body abut is set equal,
The flow rate control valve, wherein the electromagnetic actuation mechanism is configured to move the second valve body toward the first valve body when a voltage is applied to the electromagnetic coil unit .

Images