JP2013096388A - Flow control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a flow control valve capable of simplifying a structure for prevention of shaking of the flow control valve, maintaining a small controlled flow rate, and further achieving miniaturization.SOLUTION: A flow control valve includes a rotor 6 that is provided around a turning shaft 8, and rotates by electromagnetic force integrally with a turning shaft 8. The flow control valve further includes a valve body 9 that is screwed to a female screw portion 93 at one end portion side of the turning shaft 8, and opens or closes an opening portion through which fluid passes, by moving along an axial direction of the turning shaft 8 based on rotation of the turning shaft 8. The flow control valve includes a shaft supporting member 14 that is provided on the other end portion side of the turning shaft 8, and rotatably supports the turning shaft 8, as well as regulates movement toward the other end side of the turning shaft 8. The flow control valve includes a compression coil spring 10 that urges the valve body 9 toward the other end side of the turning shaft 8 along the axial direction of the turning shaft 8.

Description

  The present invention relates to a flow rate control valve including a motor and a valve that operates by rotation of the motor to control the flow rate of fluid.

  Conventionally, in a vehicle such as an automobile or a motorcycle, for example, in the case of an engine equipped with an injection that controls fuel injection and ignition by an electronic control unit, an ISCV (another throttle that is electronically controlled beside the throttle valve). (Idle speed control valve) is provided to control the idle up when the air conditioner is activated or to control the idling to be stable. That is, the ISCV controls, for example, the amount of intake air to the engine when the automobile is idling with the throttle being throttled, so that the engine reaches the target rotational speed during idling.

  The ISCV includes, for example, a stepping motor as an actuator that operates a valve, a shaft that rotates the stepping motor, and a valve body that has a screw mechanism between the shaft and moves in the axial direction of the shaft. Yes. The front end of the shaft is a male screw, and a nut fixed to the valve body is screwed into the male screw. Based on the forward and reverse rotation of the shaft, the valve body is in the axial direction of the shaft. By moving to, the flow rate of intake air to the engine during idling is controlled.

  In such an ISCV, the control flow rate is small, and a smaller flow rate is required in the normal standby position (vehicle idle state). Therefore, it is necessary to reduce the opening area of the valve (ISCV).

  Further, in the ISCV, since the control flow rate is small as described above, even if there is a slight backlash, the influence on the flow rate becomes large. Therefore, a structure (member) that suppresses rattling is required.

  Moreover, since ISCV is installed in vehicles, such as a motor vehicle and a motorcycle, for example, environmental conditions, such as a heat | fever and a vibration, are severe compared with the components installed in the fixed apparatus, and durability is required. Therefore, in the ISCV, it is necessary to use a durable bearing that supports the shaft and the rotating body in a rotatable manner.

  Here, as described above, when the influence on the control flow rate due to the vibration and rattling of the automobile is taken into account, for example, rattling can be prevented by pressing the rotating body of the valve body or the motor with a spring or the like. Conceivable. In addition, since the control flow rate is small as described above, it is basically necessary to control the movement of the valve body in a state where the valve body is close to the valve seat. For example, in the case of a flow control valve using a conical valve body, the state in which the valve body is extended toward the valve seat portion of the body of the flow control valve is maintained, thereby reducing the opening area of the valve. It is necessary to reduce the control flow rate.

  Further, as a general bearing structure in a motor, a convex bearing is provided on the rotating body side, for example, an end of a shaft protruding from the rotating body, and the concave bearing member is provided on the body (main body) side. In general, it is supported rotatably.

  As a flow control valve, for example, a valve in which a magnet is fixed to a shaft and annular dry bearings (sliding bearings) are arranged on the rear end side and the front portion of the shaft has been proposed (for example, Patent Documents). 1). In this flow control valve, the shaft is inserted in the hole of the dry bearing, and these dry bearings do not restrict the axial movement of the shaft.

  Also, as a flow control valve, a resin rotating body with a magnet fixed is supported by a ball bearing. The rotating body is placed inside an annular ball bearing, and the rotating body is fixed to the inner ring of the ball bearing. In addition, a motor-type flow control valve for an internal combustion engine in which a rotating body rotates integrally with an inner ring with respect to an outer ring of a ball bearing has been proposed (for example, see Patent Document 2). In this flow control valve, a male screw is formed on the outer periphery of the shaft and screwed into a female screw provided on the rotating body, and the shaft moves in the axial direction integrally with the valve body corresponding to the rotation of the rotating body. It is supposed to be.

JP 2008-19957 A Japanese Patent No. 3598219

  By the way, when a member such as a spring is used for the flow control valve as described above to prevent rattling, a member such as a spring is used to prevent rattling of the valve body and rattling of the rotating body (rotor). Must be used. In addition, the structure may be complicated when the rotating body rotating by the spring is prevented from rattling. For these reasons, there is a risk that the cost for preventing rattling increases, and the assembly work becomes complicated.

  Further, as described above, in the case of ISCV, since a small flow rate is controlled, in order to reduce the opening area, main control is performed in a state where the valve body side is extended and brought close to the valve seat portion of the body. At this time, if there is such rattling as described above due to the vibration of the automobile, the extended valve element side contacts the valve seat side. In this case, wear due to contact between the valve seat and the valve body occurs, the opening area increases, and the control flow rate may increase.

  Further, as described above, if the rotating body is provided with a convex portion (projecting shaft) and a concave bearing is provided on the body side, the flow control valve becomes longer only at the convex portion, resulting in poor space efficiency. Become. Note that the flow control valves described in Patent Documents 1 and 2 cannot cope with these problems.

  The present invention has been made in view of the above circumstances, and provides a flow control valve that can simplify the structure of preventing the play of the flow control valve, can maintain a small control flow rate, and can be further downsized. With the goal.

In order to achieve the object, the flow control valve according to claim 1 includes a rotatable rotating shaft;
A rotating body provided around the rotating shaft, and rotated by electromagnetic force integrally with the rotating shaft;
A valve that engages with one end of the rotating shaft and opens and closes an opening through which fluid passes by moving along the axial direction of the rotating shaft based on the rotation of the rotating shaft. Body,
A shaft support member provided on the other end side of the rotating shaft, rotatably supporting the rotating shaft, and restricting movement toward the other end side of the rotating shaft;
A bearing member provided between one end and the other end of the rotating shaft, and rotatably supporting the rotating shaft via the rotating body;
And a spring that biases the valve body toward the other end of the rotating shaft along the axial direction of the rotating shaft.

  In the first aspect of the present invention, the valve element engaged with one end side of the rotating shaft is biased toward the other end side of the rotating shaft by a spring. Thereby, it will be in the state which pressed the rotation shaft which a valve body engages to the other edge part side. That is, the urging force of the spring acting toward the other end along the axial direction acts on the rotating shaft via the valve body, and the other end of the rotating shaft is pressed against the shaft support member.

  As a result, in the same manner as when springs are provided at two locations on the valve body side and the rotating shaft (rotating body) side, the backlash of the valve body is not only suppressed by one spring, but the rotating shaft on the motor side is also provided. Further, rattling of the rotating body can be suppressed. As a result, the number of parts can be reduced and the number of springs required for assembly can be reduced to one, so that the cost can be reduced and the workability when assembling the fluid control valve can be improved.

  Further, the backlash of the valve body is suppressed by the force of the spring, and the valve body is pushed away from the valve seat side formed on the body, for example, by the biasing force of the spring. The contact by the vibration etc. to the valve seat of the valve body in the state which adjoined is suppressed. Thereby, it can suppress that the opening part which a fluid passes will become large by friction with a valve body.

The fluid control valve according to claim 2 is the invention according to claim 1,
The valve body is rotated by rotation of the rotary shaft from a female screw part provided at an axial center part of the valve body and a male screw part provided on the valve body side of the rotary shaft so as to be screwed into the female screw part. A screw mechanism that moves in the opening and closing direction of the opening is provided,
The diameter of the part except the external thread part of the said rotation shaft is made thinner than the diameter of the said external thread part.

  In the invention according to claim 2, in the configuration in which the opening is opened and closed by moving the valve body by a screw mechanism when the rotating shaft rotates, the diameter of the portion excluding the male screw portion of the rotating shaft is set. By making it smaller than the diameter of the male screw portion, it is possible to reduce the weight of the rotating shaft while ensuring the force necessary for opening and closing the valve body.

By increasing the diameter of the entire rotation shaft including the male screw portion, the force acting on the valve body from the rotation shaft can be increased, but the rotation shaft becomes heavy. Thereby, for example, there is a possibility that the response performance in the opening and closing movement of the valve body may be deteriorated due to an increase in inertia of the rotating shaft. Also, more material may be used for the rotating shaft, which may increase costs.
On the other hand, by increasing the diameter of only the male screw part and reducing the diameter of other parts, the weight of the entire rotating shaft can be reduced, thereby improving the above-mentioned response and reducing the cost. it can.

  According to a third aspect of the present invention, in the flow rate control valve according to the first or second aspect, at least the other end portion of the rotating shaft of the rotating body is formed hollow, The shaft support member supports one end of the rotating shaft in a hollow.

In the invention described in claim 3, for example, by providing a magnet, an electromagnet, or the like, a rotating body that is a rotor that rotates by electromagnetic force with respect to the stator is formed hollow. Thereby, the reduction of the inertia by weight reduction of a rotary body and the cost reduction by the reduction of material can be aimed at.
In addition, since one end portion of the rotating shaft is supported by the shaft support member in the hollow portion of the rotating body, it is not necessary to project the rotating shaft from the one end portion side of the rotating body. Even if the shape is supported by a support member such as a concave bearing, the axial length can be shortened by arranging the convex part in the hollow part, improving the space efficiency of the flow control valve. And downsizing can be achieved.

The flow control valve according to claim 4 is the invention according to any one of claims 1 to 3,
Covering the periphery of the valve body, and provided with a cylindrical body with a non-circular inner cross-section,
The valve body is provided with a wall portion extending along a circumferential direction and an axial direction of the inner peripheral surface of the body,
The wall is provided with a plurality of protrusions protruding toward the inner peripheral surface of the body and contacting the inner peripheral surface of the body along the axial direction of the body and spaced apart from each other in the circumferential direction of the body. It is characterized by being.

In the invention according to claim 4, the wall portion is disposed along the inner peripheral surface of the cylindrical body having a non-circular cross section, and the plurality of convex portions protruding from the wall portion to the inner surface of the body are in contact with the body. Are spaced apart from each other in the circumferential direction of the body. Since these convex portions are in contact with the inner peripheral surface of the body having a non-circular cross-section, the axial direction of the valve body is changed with respect to the axial direction of the body by the contact between the convex portions of the wall portion and the inner peripheral surface of the body. Tilt is suppressed. Furthermore, rotation of the valve body is restricted by the wall portion and the convex portion by the plurality of convex portions coming into contact with the inner circumferential surface of the body having a non-circular cross section at intervals in the body-circumferential direction. For example, when the valve body is opened and closed by the screw mechanism as described above, the valve body can be moved in the axial direction of the rotating shaft according to the rotation of the operating shaft by restricting the rotation of the valve body side. At this time, the convex portion of the wall portion is guided to the inner peripheral surface of the body, and the inclination of the valve body is suppressed. In this case, in addition to suppressing the backlash of the valve body as described above, it is possible to prevent the valve body from tilting in the state where the valve body and the valve seat are close to each other. It can suppress that a body touches. Thereby, the expansion of the opening part area by abrasion of a valve seat and a valve body can be prevented.
In addition, by allowing only the convex portion of the wall portion to contact the inner peripheral surface of the body, the peristaltic resistance between the inner peripheral surface of the body and the wall portion is reduced, and the valve body is smoothly moved along the axial direction. Can move.

  According to the present invention, while controlling a small flow rate, it is possible to prevent rattling of the valve body that moves in the axial direction and opens and closes the valve by a rotating shaft that rotates integrally with the rotating body of the motor at low cost. Can do. In addition, this can prevent the opening area of the valve from expanding due to wear of the valve seat and the valve body.

It is sectional drawing which shows the flow control valve of embodiment of this invention. It is a perspective view which shows the valve body of the said flow control valve.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
As shown in FIG. 1, the flow control valve of this embodiment includes a resin-made motor-side body 1 and a valve-side body 2, and a motor (stepping motor) 11 is provided on the motor-side body 1 side. A fluid (air) valve 21 is provided on the side body 2 side.

The motor-side body 1 has a main body 12 formed in a cylindrical shape with a lid and a bottom, and an inner peripheral surface of the motor-side body 1 serves as a motor stator. Two annular coils 3 along the inner peripheral surface of the main body 12 It is provided side by side along the direction. The coil 3 is supported by the coil support member 4 while being wound around the coil bobbin 5.
Inside the annular coil 3, a rotating body 6 provided with a cylindrical magnet 7 fixed to the outer periphery is provided. The rotating body 6 is a rotor that rotates with respect to the stator. A motor is constituted by the stator and the rotor, and the rotating body 6 having the magnet 7 is rotated by electromagnetic force.

  The rotating body 6 is formed in a covered cylindrical shape and is hollow inside. A rotating shaft 8 that serves as a rotation axis of the rotor passes through the lid 61 portion of the rotating body 6 and the rotating shaft 8 is fixed. Further, a cylindrical protrusion 62 having a diameter smaller than that of the cylindrical portion of the main body of the rotating body 6 is formed at the portion of the lid 61 of the rotating body 6 through which the rotating shaft 8 passes so as to be coaxial with the main body of the rotating body 6. Has been. Further, the rotating body 6 has a lid 61 portion that protrudes in a bowl shape on the outer peripheral side, and positions one end of the cylindrical magnet 7. The outer peripheral surface of the bowl-shaped portion of the lid 61 and the outer peripheral surface of the magnet 7 have substantially the same outer diameter, and are arranged coaxially.

  The rotating shaft 8 is a round bar-like member, with one end portion extending from the motor-side body 1 into the valve-side body 2 with the distal end portion of the protruding portion 62 on one end side of the rotating body 6 being substantially the center. Further, the other end portion side of the rotating shaft 8 is disposed inside the rotating body 6. In this embodiment, the other end of the rotating shaft 8 is arranged at substantially the same position (position along the axial direction) as the other end side (side without the lid) of the rotating body 6 opened.

Further, a screw is formed on the outer peripheral surface of the one end portion side of the rotating shaft 8 to form a bolt-shaped male screw portion 81. Here, a portion other than the male screw portion 81 is referred to as a shaft portion 82.
The rotating shaft 8 has a shape in which the diameter of the male screw portion 81 is larger than the diameter of the shaft portion 82, and the male screw portion 81 is expanded in diameter relative to other portions of the rotating shaft 8. As will be described later, the female thread portion 93 of the valve body 9 is screwed into the male thread portion 81.

  Further, the rotation shaft 8 has a central portion covered by the protruding portion 62 of the rotating body 6 with a radial bearing and a bearing member 13 of the body 1 that is a sliding bearing via the protruding portion 62. It is supported rotatably. In FIG. 1, the bearing member 13 is illustrated integrally with the motor-side body 1, but may be separate from the body 1.

  Further, the other end portion of the rotating shaft 8 is rotatably supported by the shaft support member 14 in a state where it is disposed inside the rotating body as described above. The shaft support member 14 functions as a sliding bearing and also functions as a radial bearing and a thrust bearing. That is, the rotation shaft 8 has its rotation center defined by the shaft support member 14, and movement in the direction from one end portion of the rotation shaft 8 toward the other end portion is restricted along the axial direction of the rotation shaft 8. Has been. The movement in the opposite direction is restricted by the compression coil spring 10 as will be described later.

  The valve body 9 has an outer peripheral surface of a tip portion that functions as a valve body formed in a truncated cone shape, and can be inserted into a through hole 22 formed in the lid 23 of the valve-side body 2 having a lid. The valve 21 is closed when the outer peripheral surface of the valve body 9 comes into contact with the inner peripheral surface of the through hole 22, and the through hole portion functions as a valve seat of the valve 21. By arranging the inner peripheral surface of the through-hole 22 as the valve seat and the outer peripheral surface of the distal end portion of the valve body 9 in close proximity, the fluid is controlled with a small flow rate.

  Further, the valve body 2 is formed with a through-hole 24 through which a fluid passes through a cylindrical portion (a cylindrical shape having a substantially oval cross section (non-circular cross section)). Air as a fluid whose flow rate is controlled by the flow rate control valve flows between the through hole 22 on the lid 23 side of the valve side body 2 and the through hole 24 of the cylindrical portion of the valve side body 2 body. ing. For example, the through hole 22 on the lid 23 side is the discharge port, and the through hole 24 of the cylindrical main body of the valve side body 2 is the suction port.

  As shown in FIGS. 1 and 2, the valve body 9 is formed in a cylindrical shape in which the distal end side of the main body is formed in a truncated cone shape as described above, and the portion excluding the distal end portion is an internal threaded portion 93 inside. Is formed. The female threaded portion 93 is a screw hole that is screwed into the male threaded portion 81 of the rotating shaft 8, and the female threaded portion 93 and the male threaded portion 81 are adapted to rotate around the axis of the rotating shaft 8. The screw mechanism which moves 9 along the axial direction of the rotating shaft 8 is comprised. Note that the movement direction is opposite due to the difference in the rotation direction. For example, when the clockwise rotation is set to the normal rotation, the rotation shaft 8 rotates in the normal rotation direction, for example, the valve element 9 is When the rotary shaft 8 moves in the direction away from the body 1 along the axial direction of the rotary shaft 8 and rotates in the counterclockwise counter-rotating direction, the valve element 9 moves in the axial direction of the rotary shaft 8. It moves in the direction which approaches body 1 along.

  Moreover, the valve body 9 is arrange | positioned inside the valve side body 2, and the valve side body 2 is formed in the covered cylinder shape. The valve-side body 2 is not formed in a cylindrical shape but is formed in a cylindrical shape having a substantially elliptical cross section.

  The valve body 9 is provided with a support plate 92 having a shape corresponding to a substantially ellipse in the cross section of the valve body 2 extending to the left and right of the rear portion of the valve body. A substantially arcuate plate-like wall portion 91 is disposed along each inner circumferential surface of the ellipse. Since the wall portion 91 is substantially along the ellipse of the cross section of the body 2, the valve body 9 including the pair of wall portions 91 does not rotate along the inner peripheral surface of the body 2. Is suppressed. As will be described later, the outer surface of the wall portion does not directly contact the inner peripheral surface of the body 2, and the convex portions 95, 96, and 97 of the wall portion contact the inner peripheral surface of the body 2 as described later. ing. The length of the substantially arcuate plate-like wall portion 91 along the axial direction of the female threaded portion 93 is ½ or more of the length along the axial direction of the female threaded portion 93 of the valve body 9 and is 2/3. It is as follows.

As described above, the wall portion 91 is long along the axial direction, and has a central portion in the general arc direction (circular direction of the ellipse) on the outer surface side, one side edge side, and the other side edge side. Long rib-like convex portions 95, 96, and 97 extending back and forth along the axial direction of the valve body 9 are formed.
The extending direction of the projections 95, 96, 97 is parallel to the axial direction of the female thread portion 93 and the axial direction of the valve body 9, and these directions are parallel to the moving direction of the valve body 9. This direction is the opening and closing direction of the valve body 9 in the fluid control valve.

  Convex portions 95, 96, 97 formed on the wall 91 of the valve body 9 abut on the inner peripheral surface of the valve body 2 to guide the valve body 9 along the moving direction of the valve body 9, The rotation of the valve body 9 is restricted. That is, by providing the convex portions 95, 96, and 97 that come into contact with the inner peripheral surface of the valve side body 2, the valve body 9 can be reliably moved in the axial direction while reducing the sliding resistance between the valve body 9 and the valve side body 2. While supporting the movement, the valve body 9 is prevented from rotating following the rotating shaft 8.

For these reasons, the valve body 9 is engaged with the inner peripheral surface of the valve-side body by the wall portion 91 and the convex portions 95, 96, 97 to restrict the rotation, and the movement direction of the valve body 9 (valve In the opening and closing direction). At this time, the wall portion 91 and the convex portions 95, 96, 97 prevent the axial direction of the valve body 9 from being inclined with respect to the axial direction of the valve-side body 2.
That is, since the wall portion 91 extends in the axial direction of the valve body 9, the valve body 9 is prevented from being inclined. As a result, the valve body 9 is tilted and is prevented from coming into contact with the inner peripheral surface of the valve seat, which is the through hole 22 in a state in which the distal end portion of the valve body 9 is inserted. Thereby, the space | interval between the internal peripheral surface of the through-hole 22 and the outer peripheral surface of the valve body 9 becomes wide by abrasion by contact with the outer peripheral surface of the valve body 9 and the internal peripheral surface of the through-hole 22, and control of small flow volume is carried out. Can be prevented from becoming difficult.

  The compression coil spring 10 is disposed as a spring between the support plate 92 of the valve body 9 and the outer portion of the through hole 22 that becomes the valve seat at the inner portion of the lid 23 of the valve body 2. The compression coil spring 10 presses the valve body 9 toward the shaft support member 14 at the bottom of the motor-side body 1 on the open side in the opening / closing direction. The compression coil spring 10 prevents rattling of the valve body 9, the rotating shaft 8, and the rotating body 6.

  The compression coil spring 10 presses the valve body 9 toward the motor-side body 1, thereby causing the rotating shaft 8, in which the male threaded portion 81 is screwed to the female threaded portion 93 of the valve body 9, to the other end side. It is pressed against the provided shaft support member 14. The shaft support member 14 also receives a load along the axial direction, and the other end portion of the rotary shaft 8 is rotatably supported by the shaft support member 14, so that the shaft support member 14 can stably rotate. .

  In such a fluid control valve, the single compression coil spring 10 described above causes the valve body 9, the rotating shaft 8 screwed to the valve body 9, the rotating body 6 rotating integrally with the rotating shaft 8, and The play with the magnet 7 can be prevented. As a result, the cost can be reduced by reducing the number of parts, and the workability can be improved. In particular, the workability is reliably improved by using only one spring that is troublesome to mount.

  Further, in addition to preventing rattling of the valve body 9 by the compression coil spring 10, the inner peripheral surface of the through hole 22 of the lid 23 of the adjacent valve body 2 and the outer peripheral surface of the distal end portion of the valve body 9 are close to each other. Even in the state, the compression coil spring 10 urges the outer peripheral surface of the valve body 9 away from the inner peripheral surface of the through hole 22, so that the inner peripheral surface of the through hole 22 and the outer peripheral surface of the valve body 9 Contact is suppressed.

  Further, the wall portion 91 of the valve body 9 is formed over a length longer than ½ of the axial length of the valve body 9, and the convex portions 95, 96, 97 on the outer surface side of the wall portion 91 are formed on the valve side body 2. The axial direction of the valve body 9 and the movement in the circumferential direction are restricted, so that the axial direction of the valve body 9 and the axial direction of the valve-side body 2 are deviated from each other. Can be suppressed. Also with this configuration, contact between the inner peripheral surface of the through hole 22 and the outer peripheral surface of the valve body 9 is suppressed.

  For these reasons, contact between the inner peripheral surface of the through-hole 22 of the valve-side body 2 serving as a valve seat and the outer peripheral surface on the distal end side of the valve body 9 is suppressed, so that the inner periphery of the through-hole 22 is reduced. It is possible to prevent the surface and the outer peripheral surface of the valve body 9 from being worn, and to suppress an increase in the opening area of the valve due to the wear.

The shaft support member 14 that receives the radial force and the thrust force receives one end of the rotating shaft 8 in the opening on the bottom side of the covered cylindrical rotating body 6, that is, in the hollow portion of the rotating body 6. Therefore, the length of the rotor including the rotating body 6 can be shortened. Thereby, size reduction of a fluid control valve can be achieved.
In this case, it can also be said that the rotating shaft 8 is shortened, and the reduction of the material constituting the rotating shaft 8 and the reduction of the members constituting the rotating body 6 by making the rotating body 6 hollow. Can do. In this case, the mass of the rotating part is reduced, the inertial force acting on the rotating body 6 and the like can be reduced, and the response performance can be improved.

  Further, the rotation shaft 8 is compared with the case where the male screw portion 81 and the shaft portion 82 are made thicker because the diameter of the male screw portion 81 that transmits the rotational motion to the valve body 9 is larger than the diameter of the shaft portion 82. Thus, the valve body 9 can be opened and closed with a stronger force. At this time, since the diameter of the shaft portion 82 is narrower than that of the male screw portion 81, the rotating shaft 8 can be reduced in weight while maintaining the transmission capability of the rotary motion by the male screw portion 81. As a result, it is possible to speed up the response performance based on the cost reduction due to the reduction of the material used for the rotating shaft 8 and the reduction of the inertia due to the mass reduction of the rotating shaft 8.

DESCRIPTION OF SYMBOLS 1 Motor side body 2 Valve side body 6 Rotating body 8 Rotating shaft 81 Male thread part 82 Shaft part 9 Valve body 10 Compression coil spring (spring)
13 Bearing member 14 Shaft support member 91 Wall portion 95, 96, 97 Convex portion

Claims (4)

A rotatable shaft,
A rotating body provided around the rotating shaft, and rotated by electromagnetic force integrally with the rotating shaft;
A valve that engages with one end of the rotating shaft and opens and closes an opening through which fluid passes by moving along the axial direction of the rotating shaft based on the rotation of the rotating shaft. Body,
A shaft support member provided on the other end side of the rotating shaft and rotatably supporting the rotating shaft;
A bearing member provided between one end and the other end of the rotating shaft, and rotatably supporting the rotating shaft via the rotating body;
A fluid control valve comprising: a spring that biases the valve body toward the other end of the rotating shaft along the axial direction of the rotating shaft. The valve body is rotated by rotation of the rotary shaft from a female screw part provided at an axial center part of the valve body and a male screw part provided on the valve body side of the rotary shaft so as to be screwed into the female screw part. A screw mechanism that moves in the opening and closing direction of the opening is provided,
2. The fluid control valve according to claim 1, wherein a diameter of a portion excluding the male screw portion of the rotating shaft is made smaller than a diameter of the male screw portion.   The at least one other end side of the rotating shaft of the rotating body is formed hollow, and the shaft support member supports the other end of the rotating shaft in the hollow of the rotating body. The fluid control valve according to claim 1 or 2. Covering the periphery of the valve body, and provided with a cylindrical body with a non-circular inner cross-section,
The valve body is provided with a wall portion extending along a circumferential direction and an axial direction of the inner surface of the body,
The wall is provided with a plurality of protrusions protruding toward the inner peripheral surface of the body and contacting the inner peripheral surface of the body along the axial direction of the body and spaced apart from each other in the circumferential direction of the body. The flow rate control valve according to claim 1, wherein the flow rate control valve is provided.

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