JP2022085348A - Motor-operated valve - Google Patents

Abstract

To achieve excellent workability of an auxiliary valve element, in a motor-operated valve in which flow rate control in a small flow rate control region of a fluid is performed by a port throttle portion between an auxiliary valve port formed on a main valve element and the auxiliary valve element in a state of fully closing a main valve port by the main valve element.SOLUTION: A guide boss portion 41 inserted into an auxiliary valve chest 3R is disposed in an auxiliary valve element 4. A high lubrication guide member 10 with which the guide boss portion 41 is slidably kept into contact, is disposed between an inner periphery of the auxiliary valve chest 3R and an outer periphery of the guide boss 41. A fluid flowing into a main valve chest 1R is allowed to flow to the inside of the high lubrication guide member 10 from a communication passage 3b. The guide boss portion 41 is made to easily slide (vertical motion) in the high lubrication guide member 10. Thus generation of noise and vibration of a motor-operated valve 100 is suppressed.SELECTED DRAWING: Figure 1

Description

The present invention relates to an electric valve.

Conventionally, there is an electric valve that controls the flow rate in a small flow rate control range and a large flow rate range. Such an electric valve is disclosed in, for example, Japanese Patent Application Laid-Open No. 2020-56472 (Patent Document 1).

FIG. 9 is a vertical cross-sectional view of the same conventional motorized valve as described above. In this conventional electric valve, the auxiliary valve body b is arranged in the auxiliary valve chamber a1 inside the main valve body a. The auxiliary valve body b has a guide boss portion b1 and a needle valve b2. The auxiliary valve body b is formed at the lower end of the rotor shaft c1 of the drive unit c. The drive unit c includes a screw feed mechanism c2, and the rotation of the rotor shaft c1 causes the auxiliary valve body b to move up and down inside the main valve body a. As a result, the needle valve b2 controls the opening degree of the auxiliary valve port a2.

Japanese Unexamined Patent Publication No. 2020-56472

In the conventional solenoid valve structure, the auxiliary valve body b moves up and down while the guide boss portion b1 is guided by the inner circumference of the auxiliary valve chamber a1 of the main valve body a. This guide portion has a role of suppressing the movement in the radial direction so that the needle valve b2 of the auxiliary valve body b does not interfere with the auxiliary valve port a2 more than necessary. However, since the guide boss portion b1 of the auxiliary valve body b and the main valve body a slide between the metals, the operability may be impaired due to wear or the like.

In the present invention, the main valve port is fully closed in the main valve body, and the flow rate control in the small flow rate control range of the fluid is performed by the port throttle portion between the sub valve port formed in the main valve body and the sub valve body. It is an object of the present invention to obtain good operability of the auxiliary valve body in the electric valve.

The electric valve of the present invention has a main valve body that is provided in the main valve chamber of the valve body and opens and closes a main valve port that opens in the main valve chamber, and the main valve in the auxiliary valve chamber formed in the main valve body. A sub-valve body formed on the body that moves in the axial direction of the sub-valve port to control the opening degree of the sub-valve port is provided, and a communication passage communicating from the main valve chamber to the sub-valve chamber is formed. The main valve port is closed in the main valve body, and the fluid flowing into the sub-valve chamber through the communication passage is allowed to flow into the sub-valve chamber at the port throttle portion in the gap between the needle valve of the sub-valve body and the sub-valve port. In an electric valve having a small flow control range for throttle, the sub-valve body includes a guide boss portion arranged in the sub-valve chamber, and is between the inner circumference of the sub-valve chamber and the outer circumference of the guide boss. It is characterized by being provided with a highly lubricious guide member to which the guide boss portion is slidably contacted.

At this time, the high lubricity guide member has a cylindrical portion separated from the inner circumference of the auxiliary valve chamber, and the electric valve is characterized in that the communication passage is opened in the communication space around the cylindrical portion. Is preferable.

Further, an electric valve characterized in that the cylindrical portion of the highly lubricity guide member surrounds the needle valve of the auxiliary valve body is preferable.

Further, a sub-valve body accommodating chamber for accommodating the sub-valve body is formed inside the high lubricity guide member, and extends in the axial direction from the communication space around the cylindrical portion to the sub-valve body accommodating chamber. An electric valve characterized by having a flow path is preferable.

According to the electric valve of the present invention, since the highly lubricious guide member to which the guide boss portion is in sliding contact is provided between the inner circumference of the auxiliary valve chamber and the outer circumference of the guide boss, the auxiliary valve body moves up and down. When this is done, the guide boss portion of the auxiliary valve body can easily slide in this highly lubricious guide member to suppress the generation of operating noise and vibration of the electric valve, and the auxiliary valve body has good operability. Is obtained.

It is a vertical sectional view of the small flow rate control range state of the electric valve of 1st Embodiment of this invention. It is a vertical sectional view of the small flow rate control range state of the electric valve of the 2nd Embodiment of this invention. It is a vertical sectional view of the small flow rate control range state of the electric valve of the 3rd Embodiment of this invention. It is a vertical sectional view of the small flow rate control range state of the electric valve of 4th Embodiment of this invention. It is a vertical sectional view of the small flow rate control range state of the electric valve of the 5th Embodiment of this invention. It is a vertical sectional view of the small flow rate control range state of the electric valve of the 6th Embodiment of this invention. It is a vertical sectional view of the small flow rate control range state of the electric valve of 7th Embodiment of this invention. It is a vertical sectional view of the small flow rate control range state of the electric valve of 8th Embodiment of this invention. It is a vertical sectional view of the small flow rate control range state of the electric valve of the 9th Embodiment of this invention. It is an enlarged sectional view of the main part of the conventional electric valve.

Next, an embodiment of the motorized valve of the present invention will be described with reference to the drawings. FIG. 1 is a vertical cross-sectional view of the small flow rate control range state of the motorized valve of the first embodiment. The concept of "upper and lower" in the following description corresponds to the upper and lower parts in the drawing of FIG. The motorized valve 100 includes a valve housing 1, a support member 2, a main valve body 3, a sub valve body 4, and a drive unit 5.

The valve housing 1 is formed of, for example, brass, stainless steel, or the like in a substantially cylindrical shape, and has a main valve chamber 1R inside thereof. A first joint pipe 11 conducting to the main valve chamber 1R is connected to one side of the outer circumference of the valve housing 1, and a second joint pipe 12 is connected to a cylindrical portion extending downward from the lower end. Further, a main valve seat 13 is formed on the main valve chamber 1R side of the second joint pipe 12 of the valve housing 1, and the inside of the main valve seat 13 is a main valve port 13a. The main valve port 13a is a cylindrical hole centered on the axis L, and the second joint pipe 12 is conducted to the main valve chamber 1R via the main valve port 13a. In the present embodiment, the main valve seat 13 is integrally formed with the valve housing 1, but the valve seat member having the main valve port is provided separately from the valve housing, and the valve seat member is provided in the valve housing. It may be assembled in a form.

A support member 2 is attached to the opening at the upper end of the valve housing 1. The support member 2 is provided on a fitting portion 21 fitted in the inner peripheral surface of the valve housing 1, a substantially columnar guide portion 22 located above and below the inside of the fitting portion 21, and an upper portion of the guide portion 22. It has an extended holder portion 23 and a ring-shaped fixing bracket 24 provided on the fitting portion 21 and made of a metal plate protruding from the outer periphery of the fitting portion 21. The fitting portion 21, the guide portion 22, and the holder portion 23 are configured as an integral product made of resin, and the fixing bracket 24 is integrally provided with the fitting portion 21 made of resin by insert molding. The fitting portion 21 of the support member 2 may be press-fitted into the valve housing 1.

Further, at the center of the holder portion 23 of the support member 2, a female screw portion 23a coaxial with the axis L and a screw hole thereof are formed, and a shaft guide hole 23b connected to the screw hole of the female screw portion 23a is formed. A cylindrical slide hole 23c having a diameter larger than the inner circumference of the shaft guide hole 23b is formed. A cylindrical rod-shaped rotor shaft 51 is arranged in the screw hole of the female screw portion 23a and the shaft guide hole 23b. A male threaded portion 51a is formed on the outer periphery of the rotor shaft 51, and the male threaded portion 51a is screwed into the female threaded portion 23a of the holder portion 23.

The holder portion 23 has a guide male screw 231 formed of a spiral protrusion on the outer periphery thereof, a lower end stopper 232 protruding radially from one lower end of the guide male screw 231 and an outer peripheral edge of the upper end portion of the guide male screw 231. The upper end stopper 233 is formed on the upper end stopper 233, respectively. Further, a coil-shaped driven slider 234 is screwed on the outer circumference of the guide male screw 231. The driven slider 234 is rotated in the same direction as the magnet rotor 52, which will be described later, rotates, and moves in the same direction (up and down) as the rotor shaft 51 following the guide male screw 231. Then, when the driven slider 234 comes into contact with the lower end stopper 232 or the upper end stopper 233, the upper and lower stop positions of the magnet rotor 52 are restricted.

The main valve body 3 is composed of a main valve portion 31 that sits and leaves the main valve seat 13, and a sub-valve inclusion portion 32 that is a side wall of the main valve body 3 and includes the sub-valve body 4. There is. A columnar opening 3A is formed inside the main valve portion 31, and a columnar sub-valve chamber 3R is formed inside the sub-valve inclusion portion 32. A cylindrical sub-valve port 3a that opens from the sub-valve chamber 3R toward the opening 3A with the axis L as the center is formed between the main valve portion 31 and the sub-valve inclusion portion 32.

A communication passage 3b that communicates from the main valve chamber 1R to the sub-valve chamber 3R is formed on the side surface of the sub-valve inclusion portion 32 of the main valve body 3 in a direction intersecting the axis L. In this embodiment, a plurality (for example, four) of the communication passages 3b are formed radially around the axis L at positions to be rotated. Further, the main valve body 3 has a retainer 34 at the upper end portion of the auxiliary valve inclusion portion 32, and also has a main valve spring 35 between the retainer 34 and the upper end portion of the guide hole 2A of the support member 2. The main valve body 3 is urged in the direction (closed direction) of the main valve seat 13 by the main valve spring 35. A muffling member 36 is arranged inside the opening 3A of the main valve portion 31. The number of the continuous passages 3b is not limited to the form in which a plurality of the continuous passages 3b are formed radially at the positions to be rotated, and the number of the continuous passages 3b may be one or a plurality of the continuous passages 3b may be formed at unequal intervals.

The auxiliary valve body 4 is formed at the lower end of the rotor shaft 51. Further, the auxiliary valve body 4 is integrally formed with the rotor shaft 51. The auxiliary valve body 4 is composed of a guide boss portion 41 and a needle valve 42. Further, the needle valve 42 of the sub-valve body 4 has its tip inserted in the axis L direction with respect to the sub-valve port 3a, and the port throttle portion which is a gap between the needle valve 42 and the sub-valve port 3a is small. Small flow rate control is performed by flowing a fluid with a flow rate. An annular washer 43 made of a lubricating resin is disposed at the upper end of the guide boss portion 41 of the auxiliary valve body 4, and the guide boss portion 41 is disposed inside the auxiliary valve inclusion portion 32. .. A highly lubricious guide member 10 with which the guide boss portion 41 is in sliding contact is disposed between the inner circumference of the auxiliary valve chamber 3R and the outer circumference of the guide boss portion 41. The auxiliary valve body 4 and the rotor shaft 51 may be formed separately and assembled.

A sealed case 55 is airtightly fixed to the upper end of the valve housing 1 by welding or the like, and inside the sealed case 55, a magnet rotor 52 having a multi-pole magnetized outer peripheral portion and a rotor shaft 51 fixed to the center thereof. And are provided. Further, a stator coil 53 is arranged on the outer periphery of the sealed case 55, and the magnet rotor 52, the rotor shaft 51, and the stator coil 53 constitute the stepping motor 5. Then, when a pulse signal is given to the stator coil 53, the magnet rotor 52 is rotated according to the number of pulses, and the rotor shaft 51 is rotated.

With the above configuration, when the stepping motor 5 is driven, the magnet rotor 52 and the rotor shaft 51 rotate, and the rotor shaft 51 together with the magnet rotor 52 is oriented in the axis L direction by the screw feed mechanism of the male screw portion 51a and the female screw portion 23a. Moving. Then, the sub-valve body 4 moves back and forth in the axis L direction, and the needle valve 42 of the sub-valve body 4 approaches or separates from the sub-valve port 3a. Further, when the sub-valve body 4 rises, the washer 43 engages with the retainer 34 of the main valve body 3 (at the upper end position of the sub-valve), and the main valve body 3 moves together with the sub-valve body 4 to move the main valve body 3 together. The main valve portion 31 of the above is separated from the main valve seat 13. As a result, the main valve port 13a is fully opened and a large flow rate range is established.

The high lubricity guide member 10 has a cylindrical shape that matches the inner surface of the sub-valve chamber 3R of the main valve body 3, and is installed at the bottom inside the sub-valve chamber 3R. The high lubricity guide member 10 is formed with a communication passage 10a at a position facing the communication passage 3b of the main valve body 3. In the small flow rate control range state of FIG. 1, the main valve body 3 is seated on the main valve seat 13, the main valve port 13a is closed, and the needle valve 42 of the sub-valve body 4 opens the sub-valve port 3a. It is controlled and small flow rate control is performed. At this time, the fluid flowing into the main valve chamber 1R from the first joint pipe 11 flows into the auxiliary valve chamber 3R through the communication passage 3b of the main valve body 3 and the communication passage 10a of the high lubricity guide member 10.

The high lubricity guide member 10 is made of a polyphenylene sulfide resin (PPS resin) containing a fluororesin, or a metal having a coating having a high lubricity such as a fluororesin. Therefore, the highly lubricious guide member 10 has high lubricity, and when the auxiliary valve body 4 moves up and down, the guide boss portion 41 of the auxiliary valve body 4 moves in the highly lubricious guide member 10. It slides easily, the generation of operating noise and vibration of the motorized valve 100 can be suppressed, and good operability of the auxiliary valve body 4 can be obtained.

FIG. 2 is a cross-sectional view of a main part of the motorized valve according to the second embodiment of the present invention. In the following second to eighth embodiments, the parts other than the main part shown in the figure are the same as those in FIG. 1 of the first embodiment. Further, in each of the following embodiments, the same members and similar elements as those in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. The difference between the second embodiment and the first embodiment is the configuration of the high lubricity guide member 20 and the auxiliary valve body 4'.

The auxiliary valve body 4'composed of a guide boss portion 41'thinner than the guide boss portion 41 of the first embodiment and a needle valve 42'longer than the needle valve 42 of the first embodiment. ing. A highly lubricious guide member 20 with which the guide boss portion 41'is in sliding contact is disposed between the inner circumference of the auxiliary valve chamber 3R and the outer circumference of the guide boss portion 41'. Further, the high lubricity guide member 20 has a cylindrical portion 20b, and the cylindrical portion 20b inserts the needle valve 42'to form a gap around the needle valve 42'. Further, the outer diameter of the cylindrical portion 20b is smaller than the inner diameter of the sub-valve inclusion portion 32, and the outer diameter of the cylindrical portion 20b is as a part of the sub-valve chamber 3R over the entire circumference between the cylindrical portion 20b and the sub-valve inclusion portion 32. Communication space 3R1 is formed. Further, a sub-valve body accommodating chamber 3R2 is formed inside the highly lubricity guide member 20 as a part of the sub-valve chamber 3R accommodating the sub-valve body 4', and the connected passage 3b of the main valve body 3 is formed. At the upper part, a communication passage 20a that communicates the communication space 3R1 and the auxiliary valve body accommodating chamber 3R2 is formed outside the cylindrical portion 20b. As a result, the fluid flowing into the main valve chamber 1R from the first joint pipe 11 flows into the communication space 3R1 through the communication passage 3b of the main valve body 3, and further from the communication passage 20a of the high lubricity guide member 20. It flows to the auxiliary valve port 3a side through the gap between the cylindrical portion 20b and the needle valve 42'in the auxiliary valve body accommodating chamber 3R2. Since the communication space 3R1 is formed over the entire circumference around the axis L, the communication passage 3b of the main valve body 3 is connected to the communication passage 20a via the communication space 3R1 regardless of the rotation position of the high lubricity guide member 20. It becomes possible to communicate with. Further, also in this second embodiment, the guide boss portion 41'slides easily in the high lubricity guide member 20, the operation noise and vibration of the motorized valve 100 can be suppressed, and the auxiliary valve body 4 ′ Good operability is obtained.

Further, since the cylindrical portion 20b surrounds the needle valve 42'of the auxiliary valve body 4', the needle valve 42'is less susceptible to the influence of the dynamic pressure of the fluid flowing out from the communication passage 3b of the main valve body 3. Vibration of the needle valve 42'can be prevented. Therefore, the flow rate of the fluid flowing through the auxiliary valve port 3a is stable. Further, after the fluid passes through the communication passage 3b (horizontal hole) of the main valve body 3, the flow path is bent in the axis L direction by the communication passage 20a (flow path) extending in the axis L direction, so that the flow velocity is reduced. As a result, the flow velocity of the fluid flowing into the auxiliary valve accommodating chamber 3R2 inside the high lubricity guide member 20 is also reduced, so that even if the fluid collides with the auxiliary valve body 4', the auxiliary valve body 4'is suppressed from vibrating. be able to.

FIG. 3 is a cross-sectional view of a main part of the motorized valve according to the third embodiment of the present invention. The auxiliary valve body 4'of this third embodiment is the same as that of the second embodiment. A highly lubricious guide member 30 with which the guide boss portion 41'is in sliding contact is disposed between the inner circumference of the auxiliary valve chamber 3R and the outer circumference of the guide boss portion 41'. The high lubricity guide member 30 is formed with a communication passage 30a facing the inner circumference of the auxiliary valve chamber 3R. Further, the high lubricity guide member 30 has a cylindrical portion 30b through which the needle valve 42'is inserted to form a gap around the needle valve 42'. Further, the outer diameter of the cylindrical portion 30b is smaller than the inner diameter of the sub-valve inclusion portion 32, and the outer diameter of the cylindrical portion 30b is as a part of the sub-valve chamber 3R over the entire circumference between the cylindrical portion 30b and the sub-valve inclusion portion 32. Communication space 3R1 is formed. Further, a sub-valve body accommodating chamber 3R2 is formed inside the highly lubricity guide member 30 as a part of the sub-valve chamber 3R accommodating the sub-valve body 4', and the upper part of the connecting passage 3c of the main valve body 3 is formed. A communication passage 30a communicating the communication space 3R1 and the auxiliary valve body accommodating chamber 3R2 is formed outside the cylindrical portion 30b. The fluid flowing into the main valve chamber 1R from the first joint pipe 11 flows into the communication space 3R1 through the communication passage 3c having a diameter larger than that of the first embodiment of the main valve body 3, and further inside the auxiliary valve inclusion portion 32. It flows through the connected passage 30a through the gap between the circumference and the outer periphery of the high lubricity guide member 30, and flows to the auxiliary valve port 3a side through the gap between the cylindrical portion 30b and the needle valve 42'. Since the communication space 3R1 is formed over the entire circumference, the communication passage 3b of the main valve body 3 can communicate with the communication passage 30a via the communication space 3R1 regardless of the rotation position of the high lubricity guide member 30. Become. Further, also in this third embodiment, the guide boss portion 41'slides easily in the high lubricity guide member 30, the operation noise and vibration of the motorized valve 100 can be suppressed, and the auxiliary valve body 4 ′ Good operability is obtained.

Further, since the cylindrical portion 30b surrounds the needle valve 42'of the auxiliary valve body 4', the needle valve 42'is less susceptible to the influence of the dynamic pressure of the fluid flowing out from the communication passage 3c of the main valve body 3. Vibration of the needle valve 42'can be prevented. Therefore, the flow rate of the fluid flowing through the auxiliary valve port 3a is stable. Further, after passing through the communication passage 3c (horizontal hole) of the main valve body 3, the fluid extends in the axis L direction between the auxiliary valve inclusion portion 32 and the high lubricity guide member 30 up to the communication passage 30a. Since the flow path is bent in the L direction of the axis due to the gap (flow path), the flow velocity is reduced. As a result, the flow velocity of the fluid flowing into the auxiliary valve accommodating chamber 3R2 inside the high lubricity guide member 30 is also reduced, so that even if the fluid collides with the auxiliary valve body 4', the auxiliary valve body 4'is suppressed from vibrating. be able to.

FIG. 4 is a cross-sectional view of a main part of the motorized valve according to the fourth embodiment of the present invention. A high lubricity guide member 40 to which the guide boss portion 41's sliding contacts is disposed between the inner circumference of the auxiliary valve chamber 3R and the outer circumference of the guide boss portion 41'. The outer shape of the high lubricity guide member 40 is the same as that of the high lubricity guide member 30 of the third embodiment, and has a cylindrical portion 40b through which the needle valve 42'is inserted to form a gap around the needle valve 42'. ing. Further, the outer diameter of the cylindrical portion 40b is smaller than the inner diameter of the sub-valve inclusion portion 32, and the outer diameter of the cylindrical portion 40b is as a part of the sub-valve chamber 3R over the entire circumference between the cylindrical portion 40b and the sub-valve inclusion portion 32. Communication space 3R1 is formed. Further, a sub-valve body accommodating chamber 3R2 for accommodating the sub-valve body 4'is formed inside the high lubricity guide member 40. Further, in the cylindrical portion 40b, a communication passage 40a is formed at a position facing the communication passage 3c of the main valve body 3. The fluid flowing into the main valve chamber 1R from the first joint pipe 11 flows into the communication space 3R1 through the communication passage 3c of the main valve body 3, and further passes through the communication passage 40a from the outer periphery of the high lubricity guide member 40. It flows to the auxiliary valve port 3a side through the gap between the cylindrical portion 40b and the needle valve 42'in the auxiliary valve body accommodating chamber 3R2. Since the communication space 3R1 is formed over the entire circumference, the communication passage 3c of the main valve body 3 can communicate with the communication passage 40a via the communication space 3R1 regardless of the rotation position of the high lubricity guide member 40. Become. Further, also in this fourth embodiment, the guide boss portion 41'can easily slide in the highly lubricity guide member 40 to suppress the generation of operating noise and vibration of the motorized valve 100, and the auxiliary valve body 4 ′ Good operability is obtained.

FIG. 5 is a cross-sectional view of a main part of the motorized valve according to the fifth embodiment of the present invention. Between the inner circumference of the auxiliary valve chamber 3R and the outer circumference of the guide boss portion 41 ′, a highly lubricious guide member 50 to which the guide boss portion 41 ′ slides into contact and a cylindrical filter F are arranged. There is. The outer shape of the high lubricity guide member 50 is substantially the same as that of the high lubricity guide member 30 of the third embodiment, and has a cylindrical portion 50b through which the needle valve 42'is inserted to form a gap around the needle valve 42'. is doing. Further, a communication passage 50a that opens to the filter F side is formed on the side portion of the high lubricity guide member 50. The fluid flowing into the main valve chamber 1R from the first joint pipe 11 flows into the communication space 3R1 through the communication passage 3c of the main valve body 3, and further flows from the outer periphery of the cylindrical portion 50b of the high lubricity guide member 50 to the filter F. And flows inside the high lubricity guide member 50 through the connected passage 50a. Further, it flows to the auxiliary valve port 3a side through the gap between the cylindrical portion 50b and the needle valve 42'. Further, also in this fifth embodiment, the guide boss portion 41'can easily slide in the high lubricity guide member 50 to suppress the generation of operating noise and vibration of the motorized valve 100, and the auxiliary valve body 4 ′ Good operability is obtained.

Further, since the cylindrical portion 50b surrounds the needle valve 42'of the auxiliary valve body 4', the needle valve 42'is less susceptible to the influence of the dynamic pressure of the fluid flowing out from the communication passage 3c of the main valve body 3. Vibration of the needle valve 42'can be prevented. Therefore, the flow rate of the fluid flowing through the auxiliary valve port 3a is stable. Further, after the fluid passes through the communication passage 3c (horizontal hole) of the main valve body 3, the flow path is bent in the axis L direction by the filter F (flow path) extending in the axis L direction up to the communication passage 50a. Therefore, the flow velocity is reduced. Further, the flow velocity is further reduced by the flow path resistance received when the fluid passes through the filter F. As a result, the flow velocity of the fluid flowing into the auxiliary valve accommodating chamber 3R2 inside the high lubricity guide member 50 is reduced, so that even if the fluid collides with the auxiliary valve body 4', the auxiliary valve body 4'is suppressed from vibrating. be able to.

FIG. 6 is a cross-sectional view of a main part of the motorized valve according to the sixth embodiment of the present invention. A high lubricity guide member 60 with which the guide boss portion 41'is in sliding contact is disposed between the inner circumference of the auxiliary valve chamber 3R and the outer circumference of the guide boss portion 41'. This sixth embodiment eliminates the filter F of the fifth embodiment, and the communication passage 3b of the main valve body 3 is the same as that of the first embodiment, and the needle valve 42'is inserted through the needle valve 42'. It has a cylindrical portion 60b that forms a gap around ′. Further, a communication passage 60a that opens into the auxiliary valve chamber 3R is formed on the side portion of the high lubricity guide member 60. The fluid flowing into the main valve chamber 1R from the first joint pipe 11 flows into the communication space 3R1 through the communication passage 3b of the main valve body 3, and further with the outer periphery of the high lubricity guide member 60 and the auxiliary valve inclusion portion 32. It passes through the gap between the spaces and flows inside the high lubricity guide member 60 through the communication passage 60a. Further, it flows to the auxiliary valve port 3a side through the gap between the cylindrical portion 60b and the needle valve 42'. Further, also in this fifth embodiment, the guide boss portion 41'slides easily in the high lubricity guide member 60, the operation noise and vibration of the motorized valve 100 can be suppressed, and the auxiliary valve body 4 ′ Good operability is obtained.

Further, since the cylindrical portion 60b surrounds the needle valve 42'of the auxiliary valve body 4', the needle valve 42'is less susceptible to the influence of the dynamic pressure of the fluid flowing out from the communication passage 3b of the main valve body 3. Vibration of the needle valve 42'can be prevented. Therefore, the flow rate of the fluid flowing through the auxiliary valve port 3a is stable. Further, the fluid passes through the communication passage 3b (horizontal hole) of the main valve body 3 and then has an axis line due to a gap (flow path) extending in the axis L direction between the auxiliary valve inclusion portion 32 and the high lubricity guide member 60. Since the flow path is bent in the L direction, the flow velocity is reduced. As a result, the flow velocity of the fluid flowing into the auxiliary valve accommodating chamber 3R2 inside the high lubricity guide member 60 is also reduced, so that even if the fluid collides with the auxiliary valve body 4', the auxiliary valve body 4'is suppressed from vibrating. be able to.

FIG. 7 is a cross-sectional view of a main part of the motorized valve according to the seventh embodiment of the present invention. Between the inner circumference of the auxiliary valve chamber 3R and the outer circumference of the guide boss portion 41 ′, a highly lubricious guide member 70 to which the guide boss portion 41 ′ slides into contact and a cylindrical filter F ′ are arranged. ing. The outer shape of the high lubricity guide member 70 is substantially the same as that of the high lubricity guide member 30 of the third embodiment, and has a cylindrical portion 70b through which the needle valve 42'is inserted to form a gap around the needle valve 42'. is doing. Further, a communication passage 70a that opens on the filter F'side is formed on the side portion of the high lubricity guide member 70. The fluid flowing into the main valve chamber 1R from the first joint pipe 11 flows into the communication space 3R1 through the communication passage 3c of the main valve body 3, and further flows from the outer periphery of the cylindrical portion 70b of the high lubricity guide member 70 to the filter F. ′, It flows to the inside of the high lubricity guide member 70 through the connected passage 70a. Further, it flows to the auxiliary valve port 3a side through the gap between the cylindrical portion 70b and the needle valve 42'. Further, also in this seventh embodiment, the guide boss portion 41'slides easily in the high lubricity guide member 70, the operation noise and vibration of the motorized valve 100 can be suppressed, and the auxiliary valve body 4 ′ Good operability is obtained.

Further, since the cylindrical portion 70b surrounds the needle valve 42'of the auxiliary valve body 4', the needle valve 42'is less susceptible to the influence of the dynamic pressure of the fluid flowing out from the communication passage 3b of the main valve body 3. Vibration of the needle valve 42'can be prevented. Therefore, the flow rate of the fluid flowing through the auxiliary valve port 3a is stable. Further, after the fluid passes through the communication passage 3c (horizontal hole) of the main valve body 3, the flow path is bent in the axis L direction by the filter F'(flow velocity) extending in the axis L direction up to the communication passage 70a. Therefore, the flow velocity is reduced. Further, the flow velocity is further reduced by the flow path resistance received when the filter F'fluid passes through. As a result, the flow velocity of the fluid flowing into the auxiliary valve accommodating chamber 3R2 inside the high lubricity guide member 70 is reduced, so that even if the fluid collides with the auxiliary valve body 4', the auxiliary valve body 4'is suppressed from vibrating. be able to.

FIG. 8 is a cross-sectional view of a main part of the motorized valve according to the eighth embodiment of the present invention. The auxiliary valve body 4 "of the eighth embodiment has a longer length than the guide boss portion 41" of the seventh embodiment and the needle valve 42 "of the seventh embodiment. It is composed of a needle valve 42 ″, and a high lubricity guide to which the guide boss portion 41 ″ slides between the inner circumference of the auxiliary valve chamber 3R and the outer circumference of the guide boss portion 41 ″. A member 80 is arranged. Similar to the second embodiment, the high lubricity guide member 80 communicates the communication space 3R1 and the sub-valve body accommodating chamber 3R2 at the upper part of the communication passage 3c of the main valve body 3. The communication passage 80a is formed. The fluid flowing into the main valve chamber 1R from the first joint pipe 11 flows into the communication space 3R1 through the communication passage 3c of the main valve body 3, and further, the high lubricity guide member 80. From the outer periphery of the cylindrical portion 80b of the above, it passes through the filter F ″, passes through the communication passage 80a, and flows inside the high lubricity guide member 80. Further, it flows to the auxiliary valve port 3a side through the gap between the cylindrical portion 80b and the needle valve 42 ″, and even in this eighth embodiment, the guide boss portion 41 ″ is easily provided in the highly lubricious guide member 80. It is possible to suppress the generation of operating noise and vibration of the motorized valve 100, and it is possible to obtain good operability of the auxiliary valve body 4 ″.

Further, since the cylindrical portion 80b surrounds the needle valve 42 ″ of the auxiliary valve body 4 ″, the needle valve 42 ″ is not easily affected by the dynamic pressure of the fluid flowing out from the communication passage 3b of the main valve body 3. Vibration of the needle valve 42 ″ can be prevented. Therefore, the flow rate of the fluid flowing through the auxiliary valve port 3a is stable. Further, the fluid flows in the axis L direction by the communication passage 80a (and the filter F ″) extending in the axis L direction to reach the communication passage 80a after passing through the communication passage 3c (horizontal hole) of the main valve body 3. The flow velocity is reduced because the fluid is bent. Further, the flow velocity is further reduced by the flow path resistance received when the fluid passes through the filter F ″. As a result, the flow velocity of the fluid flowing into the auxiliary valve accommodating chamber 3R2 inside the high lubricity guide member 80 is reduced, so that even if the fluid collides with the auxiliary valve body 4 ", the auxiliary valve body 4" is suppressed from vibrating. be able to.

FIG. 9 is a cross-sectional view of a main part of the motorized valve according to the ninth embodiment of the present invention. The sub-valve body 4 ″ of the ninth embodiment is the same as that of the eighth embodiment, and the guide boss is located between the inner circumference of the sub-valve chamber 3R and the outer circumference of the guide boss portion 41 ″. A high lubricity guide member 90 with which the portion 41 ″ is in sliding contact is arranged. The high lubricity guide member 90 is connected to the communication space 3R1 at the upper part of the communication passage 3c of the main valve body 3 as in the third embodiment. A communication passage 90a communicating with the sub-valve accommodating chamber 3R2 is formed, and a filter F1 is disposed on the sub-valve accommodating chamber 3R2 side. The fluid flows through the communication space 3R1R through the communication passage 3c of the main valve body 3, further passes through the communication passage 90a from the outer periphery of the cylindrical portion 90b of the high lubricity guide member 90, passes through the filter F1, and has high lubricity. It flows inside the guide member 90, and also flows to the auxiliary valve port 3a side through the gap between the cylindrical portion 90b and the needle valve 42 ″. Further, even in this ninth embodiment, the guide boss portion 41 ″ can easily slide in the highly lubricious guide member 90 to suppress the generation of operating noise and vibration of the motorized valve 100, and the auxiliary valve body 4 ″ Good operability is obtained.

Further, since the cylindrical portion 90b surrounds the needle valve 42 ″ of the auxiliary valve body 4 ″, the needle valve 42 ″ is not easily affected by the dynamic pressure of the fluid flowing out from the communication passage 3b of the main valve body 3. Vibration of the needle valve 42 ″ can be prevented. Therefore, the flow rate of the fluid flowing through the auxiliary valve port 3a is stable. Further, the fluid passes through the communication passage 3c (horizontal hole) of the main valve body 3 and then passes through the communication passage 90a (and the filter F1) extending in the axis L direction to reach the communication passage 90a. Is bent, so the flow velocity is reduced. As a result, the flow velocity of the fluid flowing into the auxiliary valve accommodating chamber 3R2 inside the high lubricity guide member 90 is also reduced, so that even if the fluid collides with the auxiliary valve body 4 ", the auxiliary valve body 4" is suppressed from vibrating. be able to.

In the above embodiments, in the fifth, seventh, eighth and ninth embodiments, the filters F, F', F "and F1 are provided, so that in addition to the above-mentioned effects, the sound of the fluid passing sound is heard. The pressure can be reduced.

The embodiments of the present invention have been described in detail with reference to the drawings, and other embodiments have also been described in detail. However, the specific configuration is not limited to these embodiments, and the present invention is not limited to these embodiments. It is included in the present invention even if there is a design change or the like within a range that does not deviate from the gist.

1 Valve housing 1R Main valve chamber 11 1st joint pipe 12 2nd joint pipe 13 Main valve seat 13a Main valve port L Axis line 2 Support member 23a Female thread part 3 Main valve body 31 Main valve part 32 Sub valve inclusion part 3a Sub valve port 3b Coupling passage 3c Coupling passage 3R Sub-valve chamber 3R1 Communication space 3R2 Sub-valve accommodating chamber 4 Sub-valve 41 Guide boss 42 Needle valve 5 Stepping motor 51 Rotor shaft 51a Male thread 52 Magnet rotor 53 Stator coil 4'Sub-valve Body 41'Guide boss 43'Flange 4a' Expanded space 4 ″ Sub-valve 41 ″ Guide boss 10 High lubricity guide member 20 High lubricity guide member 30 High lubricity guide member 40 High lubricity guide member 50 High lubricity guide member 60 High lubricity guide member 70 High lubricity guide member 80 High lubricity guide member 90 High lubricity guide member 100 Electric valve

Claims (4)

A main valve body that is provided in the main valve chamber of the valve body and opens and closes a main valve port that opens into the main valve chamber, and a sub-valve formed in the main valve body in the sub-valve chamber formed in the main valve body. A sub-valve body that moves in the axial direction of the port to control the opening degree of the sub-valve port is provided, and a communication passage that communicates from the main valve chamber to the sub-valve chamber is formed. It has a small flow control range in which the main valve port is closed and the fluid flowing into the sub-valve chamber through the communication passage is throttled by the port throttle portion in the gap between the needle valve of the sub-valve body and the sub-valve port. In the electric valve
The sub-valve body includes a guide boss portion arranged in the sub-valve chamber, and has high lubrication in which the guide boss portion is in sliding contact between the inner circumference of the sub-valve chamber and the outer periphery of the guide boss. An electric valve characterized by being equipped with a sex guide member. The first aspect of the present invention is characterized in that the highly lubricity guide member has a cylindrical portion separated from the inner circumference of the auxiliary valve chamber, and the communication passage is opened in a communication space around the cylindrical portion. Electric valve. The electric valve according to claim 2, wherein the cylindrical portion of the highly lubricity guide member surrounds the needle valve of the auxiliary valve body. A sub-valve accommodating chamber for accommodating the sub-valve body is formed inside the highly lubricious guide member, and a flow path extending in the axial direction from the communicating space around the cylindrical portion to the sub-valve accommodating chamber. The electric valve according to claim 2 or 3, wherein the electric valve is characterized by having.

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