WO2006064865A1

WO2006064865A1 - Electrically operated control valve

Info

Publication number: WO2006064865A1
Application number: PCT/JP2005/023023
Authority: WO
Inventors: Soichiro Tomioka; Seiichi Nakano; Hisashi Hirakawa; Toru Sakamoto; Hiroshi Uchida; Taiki Nakagawa
Original assignee: Kabushiki Kaisha Saginomiya Seisakusho
Priority date: 2004-12-15
Filing date: 2005-12-15
Publication date: 2006-06-22
Also published as: JP4541366B2; CN100510580C; CN101080601A; JPWO2006064865A1

Abstract

An electrically operated control valve, in which a valve body side spring retainer member is in contact with a stopper surface section, provided on a valve holder, to limit the movement of the valve body side spring retainer member to the lower lip section side; the valve body side spring retainer member is in contact with the stopper surface section to be separated from a valve body until a male screw shaft moves, by a distance equal to or more than a predetermined value, from a position where the valve body is seated on a valve seat section further to the valve seat section side; and, as a result, the valve body side spring retainer member and the valve body are separated, causing spring force of a compression coil not to act on the valve body. By this, wear at the surface where the valve body and the valve seat section are in contact is reduced, and leakage in a totally closed state is less likely to occur for a long period.

Description

Specification

Electric control valve technology

[0001] The present invention relates to an electric control valve, and more particularly to an electric control valve used as an expansion valve of a refrigeration cycle apparatus.

[0002] As an electric control valve used as an expansion valve or the like of a refrigeration cycle apparatus, a female screw in which a male screw portion formed on a male screw shaft (rotor shaft) that is driven to rotate by a rotor of a stepping motor is fixed to a valve housing The male screw shaft is moved in the axial direction by the screw engagement with the female screw hole of the member, and the valve body is opened and closed by the axial movement of the male screw shaft, and the valve body is moved to the valve housing. An electric control valve that fully closes a valve port by sitting on a provided valve seat is known (for example, Patent Documents 1 and 2).

[0003] In this type of electric control valve, a compression spring is provided between the male screw shaft and the valve body. In the fully closed state where the valve body is seated on the valve seat, the valve body is moved by the spring force of the compression spring. By being pressed against the valve seat, the valve closing performance is obtained.

Patent Document 1: Japanese Patent Laid-Open No. 2003-148643

Patent Document 2: Real Fairness 2-37340

Disclosure of the invention

Problems to be solved by the invention

[0004] In the conventional electric control valve, even when the valve element and the male screw shaft are rotatable relative to each other, the valve element is separated from the valve seat part when the valve element is fully seated on the valve seat part. In any state of the flow control state (control range), the spring load of the compression spring acts between the male screw shaft and the valve body, and the frictional resistance in the rotational direction between the valve body and the male screw shaft due to the spring load. As long as there is no drag (force to stop rotation) acting on the valve element, the valve element rotates with the male screw shaft.

[0005] Therefore, from the moment when the valve body is seated on the valve seat portion until the valve body is sufficiently pressed against the valve seat portion (the friction resistance force in the rotational direction between the valve body and the valve seat portion, the valve caused by the spring force). Between the body and the male screw shaft Until the friction resistance in the rotational direction becomes larger), the valve body slides around while being pressed against the valve seat by the spring force. For this reason, the wear of the contact surface between the valve body and the valve seat becomes a problem, especially when repeated operating conditions are required, the wear of the contact surface between the valve body and the valve seat becomes severe. Causes a fully closed leak.

[0006] The problem to be solved by the present invention is that, in the electric control valve, the valve body is prevented from sliding while being pressed against the valve seat portion, and the contact surface between the valve body and the valve seat portion is avoided. This is to reduce the wear and prevent the occurrence of fully closed leakage over a long period of time.

Means for solving the problem

[0007] According to the present invention, a male screw portion formed on a male screw shaft that is rotationally driven by a rotor of a stepping motor is screw-engaged with a female screw hole of a female screw member fixed to the valve housing, and the screw engagement causes the above-described screw engagement. The male screw shaft moves in the axial direction, the valve body is opened and closed by the axial movement of the male screw shaft, and the valve body is seated on the valve seat portion provided in the valve housing, so that the valve port is fully closed. In the electric control valve, the male screw shaft and the valve body are connected to each other so as to be relatively displaceable in the axial direction by a cylindrical valve holder disposed in the valve housing so as to be movable in the axial direction. When seated on the valve seat portion, no spring load is generated to press the valve body against the valve seat portion, and the valve body is further moved when the male screw shaft has moved a predetermined amount or more in the valve closing direction. To produce a spring load to press the valve seat, it is possible to provide a motorized control valve compression spring is incorporated within the valve holder.

[0008] Further, according to the present invention, the male screw portion formed on the male screw shaft that is rotationally driven by the rotor of the stepping motor is screw-engaged with the female screw hole of the female screw member fixed to the valve housing. The male screw shaft moves in the axial direction, the valve body is opened and closed by moving the male screw shaft in the axial direction, and the valve body is seated on the valve seat portion provided in the valve housing, so that the valve port is fully closed. The electric control valve has a cylindrical valve holder disposed in the valve housing so as to be movable in the axial direction, and the valve body is attached to the valve holder so as to be displaceable in the axial direction. When the valve body engages with a lower side surface portion formed at one end of the valve body, the valve body is suspended and supported from the valve holder, and is suspended at the tip of the male screw shaft. Engaging portion wherein By engaging with the upper side surface formed at the other end of the valve holder, the valve holder is supported by being suspended from the male screw shaft, and a valve body side spring retainer member is provided in the valve holder. The suspension engaging portion of the male screw shaft and the valve body side spring retainer member are provided so as to be movable in the axial direction in a state in which the movement toward the lower side surface portion side is restricted by abutting against the received stagger portion. A compression spring is attached between the valve body and the valve body from a state where the valve body is separated from the valve seat portion and a state where the valve body is seated on the valve seat portion by movement of the male screw shaft in the valve closing direction. Until the holder moves more than a predetermined value relative to the valve body toward the valve seat part, the valve body side spring retainer member comes into contact with the strobe part and is separated from the valve body, and the valve body side Spring retainer The material is separated from the valve body, and the spring force of the compression spring does not act on the valve body, and the valve body is seated on the valve seat portion by the movement of the male screw shaft in the valve closing direction. In a state in which the valve holder moves relative to the valve body relative to the valve body by a predetermined value or more due to movement of the male screw shaft in the valve closing direction, the valve body side spring retainer member is moved from the stagger portion. It is possible to provide an electric control valve that abuts against the valve body in a separated state and applies a spring force of the compression spring to the valve body.

Further, according to the present invention, a male screw portion formed on a male screw shaft that is rotationally driven by a rotor of a stepping motor is screw-engaged with a female screw hole of a female screw member fixed to the valve housing, and the male screw shaft is caused by the screw engagement. Electric control that moves in the axial direction, opens and closes the valve body by moving in the axial direction of the male screw shaft, and fully closes the valve port when the valve body is seated on the valve seat provided in the valve housing. The valve has a cylindrical valve holder disposed in the valve housing so as to be movable in the axial direction. The valve body is fixedly attached to one end of the valve holder, and is attached to the tip of the male screw shaft. The formed suspension engaging portion engages with the upper side surface portion formed at the other end of the valve holder, so that the valve holder is suspended and supported from the male screw shaft, and the valve ho A screw shaft side spring retainer member is provided in the slider so as to be movable in the axial direction in a state where movement to the side surface portion side is restricted by the spacer member provided in the valve holder, A compression spring is attached between the screw shaft side spring retainer member and the valve body, and the valve body is separated from the valve seat portion and moved in the valve closing direction of the male screw shaft. Thus, the operation of the spacer member is continued until the male screw shaft moves more than a predetermined value relative to the valve holder from the state in which the valve body is seated on the valve seat portion. As a result, the tip of the male screw shaft is separated from the screw shaft side spring retainer member, so that the spring force of the compression spring does not act as a valve closing spring load on the valve holder and the valve body, and the valve body In the state where the male screw shaft is moved more than a predetermined value relative to the valve holder by the valve closing direction movement of the male screw shaft from the state where the male screw shaft is seated on the valve seat portion, the male screw An electric control valve can be provided in which the tip of the shaft abuts against the screw shaft side spring retainer member to apply the spring force of the compression spring to the valve body.

Further, according to the present invention, a male screw portion formed on a male screw shaft that is rotationally driven by a rotor of a stepping motor is screw-engaged with a female screw hole of a female screw member fixed to the valve housing, and the male screw shaft is caused by the screw engagement. Electric control that moves in the axial direction, opens and closes the valve body by moving in the axial direction of the male screw shaft, and fully closes the valve port when the valve body is seated on the valve seat provided in the valve housing. The valve has a cylindrical valve holder disposed in the valve housing so as to be movable in the axial direction. The valve body is attached to the valve holder so as to be displaceable in the axial direction. The valve body is suspended and supported from the valve holder by engaging the lower surface portion formed at the end portion, and the suspension member is formed at the tip of the male screw shaft. When the portion engages with an upper side surface formed at the other end of the valve holder, the valve holder is supported so as to be rotatable from the male screw shaft, and a screw shaft side spring retainer is supported in the valve holder. The member is provided to be movable in the axial direction in a state where movement to the upper side surface side is restricted by a spacer member provided in the valve holder, and the screw shaft side spring retainer member and the valve A compression spring is attached between the valve body and the male screw from a state where the valve body is separated from the valve seat portion and a state where the valve body is seated on the valve seat portion by movement of the male screw shaft in a valve closing direction. The distal end of the male screw shaft is moved by the action of the spacer member until the male screw shaft moves relative to the valve body toward the valve seat by a valve closing direction movement. The screw shaft side spring When the retainer member is not pressed, the spring force of the compression spring is applied to the valve body. When the male screw shaft is not moved as a closed spring load and the male screw shaft is moved more than a predetermined value relative to the valve body from the state where the valve body is seated on the valve seat part, An electric control valve can be provided in which the distal end of the male screw shaft abuts on the screw shaft side spring retainer member to apply the spring force of the compression spring to the valve body.

[0011] Further, as one preferred embodiment, an electric control valve in which the valve body is provided so as to be displaceable in a radial direction with respect to the valve holder can be provided.

[0012] Further, as one preferred embodiment, an electric control valve in which the male screw shaft and the valve holder are provided so as to be displaceable in the radial direction can be provided.

[0013] Further, preferably U, as one embodiment, the valve body has a valve stem portion at a portion protruding to the valve seat portion side from the valve holder, and the valve stem portion is attached to the valve housing. It is possible to provide an electric control valve that is fitted to an installed stem guide portion so as to be displaceable in the axial direction, and the valve stem portion is guided and supported by the valve housing.

In the electric control valve according to the present invention, when the valve body is seated on the valve seat portion, no spring load is generated to press the valve body against the valve seat portion, and the male screw shaft further exceeds a predetermined amount in the valve closing direction. A spring force that presses the valve body against the valve seat when moving is generated, so the frictional force generated between the valve body and the valve seat when the valve body is seated on the valve seat and when the valve body is released is The amount of wear is extremely small even when repeated operations are performed because of the weight of the valve body or the valve body and the valve holder.

Brief Description of Drawings

FIG. 1 is a longitudinal sectional view showing Embodiment 1 of an electric control valve according to the present invention.

FIG. 2 is a longitudinal sectional view of a main part showing an operating state 1 of the electric control valve according to the first embodiment.

FIG. 3 is a longitudinal sectional view of a main part showing an operating state 2 of the electric control valve according to the first embodiment.

[FIG. 4] A longitudinal section of the main part showing the operating state 3 of the electric control valve according to Embodiment 1. FIG.

FIG. 5 is a longitudinal sectional view of a main part showing an operating state 4 of the electric control valve according to the first embodiment.

[FIG. 6] (a) to (c) are drawings showing operating characteristics of the electric control valve according to the first embodiment.

FIG. 7 is a longitudinal sectional view showing a modification of the electric control valve according to the first embodiment.

FIG. 8 is a longitudinal sectional view showing a modification of the electric control valve according to the first embodiment.

FIG. 9 is a longitudinal sectional view showing a modification of the electric control valve according to the first embodiment.

FIG. 10 is a longitudinal sectional view showing a modification of the electric control valve according to the first embodiment.

FIG. 11 is a longitudinal sectional view showing a modification of the electric control valve according to the first embodiment.

FIG. 12 is an enlarged longitudinal sectional view of a main part showing a modification of the electric control valve according to Embodiment 1.

FIGS. 13 (a) and 13 (b) are enlarged longitudinal sectional views of essential parts showing a modification of the electric control valve according to Embodiment 1. FIG.

FIG. 14 is a longitudinal sectional view showing Embodiment 2 of the electric control valve according to the present invention.

FIG. 15 is a longitudinal sectional view of a main part showing an operating state 1 of the electric control valve according to the second embodiment.

FIG. 16 is a longitudinal sectional view of a main part showing an operating state 2 of the electric control valve according to the second embodiment.

FIG. 17 is a longitudinal sectional view of a main part showing an operating state 3 of the electric control valve according to the second embodiment.

FIG. 18 is a longitudinal sectional view of essential parts showing an operating state 4 of the electric control valve according to the second embodiment.

[FIG. 19] (a) to (c) are graphs showing operating characteristics of the electric control valve according to the second embodiment.

FIG. 20 is a longitudinal sectional view showing a modification of the electric control valve according to the second embodiment.

FIG. 21 is a longitudinal sectional view showing a modified example of the electric control valve according to the second embodiment. FIG. 22 is a longitudinal sectional view showing Embodiment 3 of the electric control valve according to the present invention.

FIG. 23 is an enlarged longitudinal sectional view of a main part of the electric control valve according to Embodiment 3.

FIG. 24 is a locally enlarged longitudinal sectional view of a main part of the electric control valve according to Embodiment 3.

FIG. 25 is a longitudinal sectional view of a main part showing an operating state 1 of the electric control valve according to the third embodiment.

FIG. 26 is a longitudinal sectional view of essential parts showing an operating state 2 of the electric control valve according to the third embodiment.

FIG. 27 is a longitudinal sectional view of an essential part showing an operating state 3 of the electric control valve according to the third embodiment.

FIG. 28 is a longitudinal sectional view of essential parts showing an operating state 4 of the electric control valve according to the third embodiment.

[FIG. 29] (a) to (c) are graphs showing operating characteristics of the electric control valve according to the third embodiment.

FIG. 30 is an explanatory diagram showing the effectiveness of the electric control valve according to the third embodiment.

FIG. 31 is an enlarged longitudinal sectional view of a main part showing a modification of the electric control valve according to Embodiment 3.

FIG. 32 is a longitudinal sectional view showing a modification of the electric control valve according to the third embodiment. Explanation of symbols

10 Valve housing

11 Valve chamber

12 Valve port

13 Horizontal joint

14 Inlet port

15 Lower joint

16 Exit port Fixed support member

Guide hole

, 20A, 20B, 20C, 40, 40A Valve holder, 21A Lower lip piece

Lower member

, 23A, 41 Upper lip piece

Upper member

Stopper surface

, 27, 42 opening

ヮ sha

Valve seat surface

50, 90 Disc

, 34, 52

Annular steps

51 Flow rate adjuster

Valve body side spring retainer member

A Bottom bottom

, 46 compression coil spring

Male thread

Female thread

47 Spacer members

A Spacer section

B Washer

Screw shaft side spring retainer member

High lubricity washer

Packing

O-ring groove

O-ring Valve seat member

Hemispherical receiving member, 65 sphere

Top

, 66 Hemispherical recess Hemispherical seat member Stepping motor Rotor case Rotor

A Outer peripheral surface

Male screw shaft

Bottom

, 83 Suspension engagement part Upper end part

Stator coil unit Guide support shaft

A Bearing hole

Spiral guide wire body Fixed stopper part Movable stopper member Projection part

Valve stem

Upper flange part Spacer member

A Spacer section

ヮ sha

A

Bottom member 96 Screw shaft side spring retainer

97 Guide hole

98 Stem guide member

99 Lower lid member

101 opening

102 High-slip washer

103, 104, 105 Pressure equalizing hole

106 Pressure equalizing spiral groove

BEST MODE FOR CARRYING OUT THE INVENTION

[0017] Preferred embodiments of the present invention will be described with reference to the accompanying drawings.

[0018] (Embodiment 1 of electric control valve)

Embodiment 1 of an electric control valve according to the present invention will be described with reference to FIG.

The electric control valve has a valve housing 10 made of a cup-shaped metal or synthetic resin. The valve housing 10 includes a valve chamber 11, a round hole shaped valve port 12 formed in the lower bottom of the valve chamber 11, an inlet port 14 connected to the lateral joint 13 and directly communicating with the valve chamber 11, and a lower joint. 15 and an outlet port 16 communicating with the valve chamber 11 via the valve port 12.

A fixed support member (female screw member) 18 is fixed to the upper portion of the valve housing 10 by a mounting plate 17. A guide hole 19 is formed in the fixed support member 18. The guide hole 19 is concentric with the valve port 12, and a cylindrical valve holder 20 is fitted in the guide hole 19 so as to be slidable in the axial direction (up and down direction), that is, in the valve opening / closing direction. Thereby, the valve holder 20 can move in the valve housing 10 in the axial direction.

[0021] The valve holder 20 is composed of a lower member 22 having an annular lower lip piece 21 forming a lower side surface portion at a lower end, and an upper member having an annular upper lip piece 23 forming an upper side surface portion at an upper end. 24, and has an annular stopper-like upward stopper surface portion 25 at the connecting portion between the lower member 22 and the upper member 24.

[0022] On the lower member 22 of the valve holder 20, a metal or synthetic resin valve body 30 is provided in the axial direction. It is attached to be displaceable. The valve body 30 is loosely fitted into the opening 26 formed in the lower member 22, that is, fitted with a predetermined radial gap so that it can be displaced in the radial direction with respect to the valve holder 20. An annular stepped portion (shoulder portion) 32 is suspended and supported rotatably from the valve holder 20 by engaging the lower surface of the lower lip piece 21. The valve body 30 has a conical flow control part (needle valve part) 33 on the lower side, and the flow control part 33 is directed from the opening 26 inside the lower lip piece 21 toward the valve port 12. Protruding.

[0023] The valve body 30 is a circle formed at the base of the flow rate adjusting unit 33 by performing quantitative flow rate control in accordance with the degree of penetration (position in the axial direction) of the flow rate adjusting unit 33 with respect to the valve port 12. When the annular fully closed surface portion 34 is adhered to the valve seat surface portion 29 around the valve port 12, the valve port 12 is closed (closed) to be fully closed.

[0024] In the valve holder 20, a lower end portion 74 of a male screw shaft 73 that forms a rotor shaft of a stepping motor 70 described later passes through an opening 27 inside the upper lip piece 23 of the upper member 24 in a loosely fitted state. Yes. This loose fitting state means that the valve holder 20 and the male screw shaft 73 can be relatively displaced in the radial direction.

[0025] At the lower end 74 of the male screw shaft 73, that is, at the tip of the male screw shaft 73, a flange-like hanging engagement portion 75 that also serves as a spring retainer is formed. The suspension engagement part 75 is rotated on the upper lip piece 23 of the valve holder 20 with a washer 28 that is coated with a highly slippery plastic such as fluorine resin or a slippery plastic cover on the upper surface side. Engaged as possible. By this engagement, the valve holder 20 is suspended and supported so as to be rotatable from the male screw shaft 73.

[0026] A valve body side spring retainer member 35 is provided in the valve holder 20 so as to be movable in the axial direction. The valve body side spring retainer member 35 is restricted from moving toward the lower lip piece 21 by abutting against a stopper surface portion 25 provided in the valve holder 20 with a lower bottom surface 35A.

Due to this limitation, as shown in FIG. 1, in a state in which the valve body 30 is located at the lowest lowered position where the annular step portion 32 of the valve body 30 contacts the lower lip piece 21, When the lower bottom surface 35A of the valve body side spring retainer member 35 is in contact with the stopper surface portion 25, a gap tl is generated between the valve body 30 and the valve body side spring retainer member 35, and the valve body side spring retainer member 35 and the valve body 30 But Disconnected.

[0028] A compression coil spring 36 is attached with a predetermined preload between the suspension engagement portion 75 forming the screw shaft side spring retainer member and the valve body side spring retainer member 35.

[0029] A male screw portion 37 is formed on the male screw shaft 73. The male threaded portion 37 is threadedly engaged with a female threaded portion (female threaded hole) 38 formed in the fixed support member 18. By this screw engagement, the male screw shaft 73 moves in the axial direction, that is, in the valve opening / closing direction with rotation.

The feed screw mechanism is configured by the screw engagement between the male screw portion 37 and the female screw portion 38, and the feed screw mechanism converts the rotational motion of the male screw shaft 73 into a linear motion in the valve opening / closing direction.

[0031] A can-shaped rotor case 71 of a stepping motor 70 is airtightly fixed to the upper portion of the valve housing 10 by welding or the like. In the rotor case 71, a rotor 72 having a multi-pole magnetized outer peripheral surface portion 72A is rotatably provided. The rotor 72 also serves as a rotor shaft! And an upper end portion 76 of a male screw shaft 73 is fixedly connected.

A stator coil unit 77 is inserted and attached to the outside of the rotor case 71.

Although not shown in detail, the stator coil unit 77 has a well-known airtight mold structure having magnetic pole teeth, a winding portion, and an electric wiring portion inside as a stepping motor.

In the rotor case 71, a guide support shaft 78 suspended and fixed from the ceiling portion of the rotor case 71, a spiral guide wire 79 attached to the outer periphery of the guide support shaft 78, and an upper end portion of the guide support shaft 78 A fixed stopper portion 80 formed on the movable guide member 80, a movable stopper member 81 screwed into the spiral guide wire 79, and a protrusion portion 82 of the rotor 72 that engages and kicks the movable stopper member 81, thereby opening the valve Alternatively, a valve closure valve is configured.

The stepping motor 70 rotationally drives the male screw shaft 73 by the rotor 72, and moves the valve body 30 along with the valve holder 20 in the valve opening / closing direction linearly by the axial movement of the male screw shaft 73 accompanying the rotation. As a result, the axial position of the flow rate adjustment part 33 of the valve body 30 relative to the valve port 12 (the linear movement position in the valve opening and closing direction) changes, and the effective opening area of the valve port 12 increases or decreases depending on the axial position. Quantitative flow control is performed.

[0035] Due to the downward movement of the valve body 30 in the valve opening / closing direction, the effective opening area of the valve port 12 is gradually reduced. Accordingly, the flow rate of the fluid flowing through the valve port 12 is gradually reduced. When the valve body 30 moves downward by a predetermined amount in the valve opening / closing direction, the fully closed surface portion 34 of the valve body 30 is in contact with the valve seat surface portion 29, so that the valve port 12 is closed.

It should be noted that pressure equalizing holes 103, 104, and 105 are formed in each part of the mounting plate 17, the fixed support member 18, and the valve holder 20.

[0037] Next, the operation of the electric control valve according to Embodiment 1 will be described in detail with reference to Figs.

FIG. 6 (a) shows the relationship between the number of pulses of the stepping motor 70 and the axial displacement of the male screw shaft 73 and the valve holder 20 and the valve element 30 in this embodiment, and FIG. 6 (b) shows the stepping motor 70. Fig. 6 (c) shows the relationship between the number of pulses of the stepping motor 70 and the flow rate. Fig. 6 (c) shows the relationship between the number of pulses of the stepping motor 70 and the flow rate. In FIG. 6 (a), L73 & 20 indicates the displacement of the male screw shaft 73 and the valve holder 20, and L30 indicates the displacement of the valve body 30. 6 (a) to (c), (1) shows the operating state of FIG. 2, (2) shows the operating state of FIG. 3, (3), (4) shows the operating state of FIG. And (5) show the operation states of FIG.

FIG. 2 shows a valve open state (control region) in which the fully closed surface portion 34 of the valve body 30 is separated from the valve seat surface portion 29. In this valve open state, the suspension engaging portion 75 of the male screw shaft 73 is engaged with the upper lip piece 23 of the valve holder 20 with the busher 28 interposed therebetween, and the valve holder 20 is suspended from the male screw shaft 73. The lower lip piece 21 is engaged with the annular step portion 32 of the valve body 30, and the valve body 30 is suspended from the valve hono-redder 20.

[0040] When the valve is in the open state, the valve body side spring retainer member 35 abuts against the stopper surface portion 25 and is separated from the valve body 30, and a gap tl exists between the valve body 30 and the valve body side spring retainer member 35. Thus, in the valve open state, the valve body side spring retainer member 35 and the valve body 30 are disconnected, and the spring force of the compression coil spring 36 does not act on the valve body 30 (state (1) in FIG. 6). Under this condition, the valve body 30 can freely rotate relative to the valve holder 20.

[0041] From this valve open state, the male screw shaft 73 is driven to rotate in the valve closing direction by the stepping motor 70, so that the male screw shaft 73, the valve holder 20, and the valve body 30 all move down. Due to this lowering, as shown in FIG. 3, the fully closed surface 34 of the valve body 30 is seated on the valve seat surface 29. (State (2) in Fig. 6).

[0042] At the moment when the fully closed surface portion 34 of the valve body 30 is seated on the valve seat surface portion 29, a gap tl continues to exist between the valve body 30 and the valve body side spring retainer member 35, and the spring of the compression coil spring 36 Since the force does not act on the valve body 30, even when the valve holder 20 and the valve body 30 are rotated by the rotation of the male screw shaft 73, when the fully closed surface portion 34 of the valve body 30 is seated on the valve seat surface portion 29, The valve body 30 does not rotate due to the friction of its own weight due to the contact between the fully closed surface portion 34 and the valve seat surface portion 29.

That is, even when the valve holder 20 is rotating, the fully closed surface portion 34 of the valve body 30 is seated without sliding around the valve seat surface portion 29.

[0044] At this time, even if the fully closed surface portion 34 of the valve body 30 rotates with respect to the valve seat surface portion 29, only a frictional resistance corresponding to the weight of the valve body 30 is generated. The contact surface between the fully closed surface portion 34 and the valve seat surface portion 29 is not large and worn.

[0045] Further, since the spring force of the compression coil spring 36 is not applied to the valve body 30, the valve body 30 can be freely displaced in the radial direction with respect to the valve holder 20 when the valve is opened to seated. Even if the valve seat surface part 29 (valve port 12) is misaligned, the valve body 30 is automatically aligned by the flow rate adjustment part 33 of the valve body 30 entering the valve port 12, etc. 34 is not in contact with the valve seat surface 29 when it is in one-sided contact, and the valve body 30 is always seated on the valve seat surface 29 in an appropriate position and posture.

If the male screw shaft 73 is further rotated in the valve closing direction by the stepping motor 70 from the state in which the fully closed surface portion 34 of the valve body 30 is seated on the valve seat surface portion 29, the fully closed surface portion of the valve body 30 The male screw shaft 73 and the valve holder 20 both move downward while 34 is seated on the valve seat surface 29.

[0047] By this downward movement, the gap between the valve body 30 and the valve body side spring retainer member 35 is narrowed, and the fully closed surface portion 34 of the valve body 30 is seated on the valve seat surface portion 29 by the movement of the male screw shaft 73 in the valve closing direction. If the valve holder 20 moves to the valve seat surface part 34 side relative to the valve body 30 from the above state by a predetermined value or more, the valve body side spring retainer member 35 is moved to the valve body 30 as shown in FIG. (State (3) in Fig. 6).

[0048] Until the moment when the valve body side spring retainer member 35 contacts the valve body 30, the compression coil spring 36 Even when the valve holder 20 that does not act on the valve body 30 is rotated, the fully closed surface portion 34 of the valve body 30 is against the valve seat surface portion 29 and the load of the closed spring of the compression coil spring 36 is reduced. Do not slid under the action!

[0049] At the moment when the valve body side spring retainer member 35 contacts the valve body 30, the spring force of the compression coil spring 36 acts on the valve body 30 (state (4) in FIG. 6), and the spring of the compression coil spring 36 Due to the force, the fully closed surface portion 34 of the valve body 30 is pressed against the valve seat surface portion 29, where a valve closing spring load is generated and valve closing performance is obtained.

As described above, after the fully closed surface portion 34 of the valve body 30 is seated on the valve seat surface portion 29, the spring force of the compression coil spring 36 acts on the valve body 30. In a state of being pressed against the valve seat surface portion 29 by the spring force of the compression coil spring 36, it does not slide around with a large frictional force against the valve seat surface portion 29.

[0051] In the valve opening process, when the fully closed surface portion 34 of the valve body 30 is separated from the valve seat surface portion 29, the valve seat surface portion 29 is similarly pressed against the valve seat surface portion 29 by the spring force of the compression coil spring 36. Therefore, the frictional resistance of the valve body 30 is only caused by the weight of the valve body 30 so that the valve body 30 does not slide around the valve seat surface 29. Wear on the contact surface with the surface portion 29 is reduced.

That is, the frictional force generated between the valve body 30 and the valve seat surface portion 34 at the moment when the fully closed surface portion 34 of the valve body 30 is seated on the valve seat surface 29 and at the moment of separation is It is only due to its own weight, and even if it is repeatedly operated, the amount of wear is extremely small.

[0053] As a result, even if repeated operating conditions are required, the closed surface leakage of the valve element 30 and the valve seat surface part 29 will not be worn out. Excellent valve closing performance can be obtained.

[0054] Further, as described above, the valve body 30 in which the fully closed surface portion 34 of the valve body 30 does not come into contact with the valve seat surface portion 29 in a single contact state is always in an appropriate position and posture. Therefore, it is possible to obtain an excellent valve closing performance that does not cause a fully closed leak.

[0055] As a result, when the male screw shaft 73 is driven to rotate in the valve closing direction by the stepping motor 70, the lower lip piece 21 of the valve holder 20 is attached to the valve body 30 as shown in FIG. Annular ring Aside from the stepped part 32, the stopper face part 25 of the valve holder 20 is the valve body side spring retainer part. The state in which the spring force of the compression coil spring 36 acts on the valve body 30 continues away from the lower bottom surface 35A of the material 35, and the reference point in the fully closed state is performed (state (5) in FIG. 6).

(Modification of Embodiment 1)

A modified example (another embodiment) of the electric control valve according to the first embodiment will be described with reference to FIGS. 7 to 13, parts corresponding to those in FIG. 1 are denoted by the same reference numerals as those in FIG. 1 and description thereof is omitted.

[0057] In the embodiment shown in Fig. 7, an annular rubber-like coasting knock 55 is mounted as a coasting seal member at the root of the flow rate adjustment section 33 of the valve body 30, and the packing is provided. 55 forms a practical total closed surface 34.

[0058] The rubber-like elastic material constituting the knockin 55 is a material exhibiting rubber-like elasticity, and the rubber-like elastic material indicates a rubber-like substance. Examples of rubber-like elastic bodies suitable for knockin 55 include vulcanized rubber, silicone rubber (Q), urethane rubber (U), fluoro rubber (FKM), and ethylene-propylene copolymer elastomer (EPM). Further, not only rubber, but also a grease material such as PTFE, PFA, nylon (registered trademark), PPS, and PEEK may be used.

In this embodiment, when the nozzle / kin 55 is pressed against the valve seat surface portion 29, the fully closed state is obtained, and the fully closed leakage is further less likely to occur. In addition, since the friction on the contact surface is small, excellent valve closing performance can be obtained over a long period of time when the wear of the packing 55 is small. This embodiment can be similarly applied to the second embodiment.

[0060] In the embodiment shown in FIG. 8, instead of the valve holder 20, a cylindrical lower lip piece 21A is provided at the lower end and an annular upper lip piece 23A is provided at the upper end. Valve holder 20A is used. A stopper surface portion 25 is formed to project in the radial direction at the intermediate portion in the valve holder 20A.

Further, a valve seat surface portion 29 around the valve port 12 is formed so as to protrude one step from the outer peripheral portion, and an O-ring groove 56 is formed in the valve seat surface portion 29. The O-ring groove 56 is provided with an O-ring 57 made of a rubber-like inertia material as an elastic seal member.

[0062] The rubber-like elastic material constituting the O-ring 57 is a material exhibiting rubber-like elasticity, and refers to rubber or a rubber-like substance. Rubber-like elastic bodies suitable for O-ring 57 include vulcanized rubber, silicone rubber (Q), urethane rubber (U), fluoro rubber (FKM), and ethylene propylene copolymer system. The last (EPM) etc. are mentioned. Not only rubber, but also PTFE, PFA, nylon (registered trademark), PPS, PEEK, etc.

In this embodiment, when the fully closed surface portion 34 of the valve body 30 is pressed against the O-ring 57, the fully closed state is obtained, and the fully closed leakage is further less likely to occur. In addition, since the friction on the contact surface is small, excellent valve closing performance can be obtained over a long period of time when the wear of the O-ring 57 is small. Note that the characteristic components of this embodiment can be similarly applied to those of Embodiments 2 and 3 described later.

[0064] In the embodiment shown in FIG. 9, a valve seat member 58 made of a rubber-like inertia material as an elastic seal member is provided so as to cover a surface portion from the valve seat surface portion 29 to the valve port 12. A configuration is adopted in which the valve seat member 58 is attached to the ring 10 and the valve seat member 58 defines the valve port 12 and the valve seat surface portion 29 around it.

[0065] The rubber-like inertia material constituting the valve seat member 58 is a material exhibiting rubber-like elasticity, and indicates a rubber or a rubber-like substance. Examples of rubber-like elastic bodies suitable for the valve seat member 58 include vulcanized rubber, silicone rubber (Q), urethane rubber (U), fluoro rubber (FKM), and ethylene-propylene copolymer elastomer (EPM). Further, not only rubber, but also a grease material such as PTFE, PFA, nylon (registered trademark), PPS, and PEEK may be used.

[0066] In this embodiment, the fully closed surface portion 34 of the valve body 30 is pressed against the valve seat surface portion 29 by the valve seat member 58 made of rubber-like coasting material, whereby a fully closed state is obtained, and the fully closed leakage is Even less likely to occur. Further, since the friction of the contact surface is small, excellent valve closing performance can be obtained over a long period of time when the wear of the valve seat surface portion 29 by the valve seat member 58 is small. Note that the characteristic components of this embodiment can be similarly applied to those of Embodiments 2 and 3 described later.

[0067] In any of the embodiments shown in Figs. 7 to 9, a gap tl is provided between the valve body 30 and the valve body side spring retainer member 35. The same effects as those of the first embodiment can be obtained.

[0068] In the embodiment shown in FIG. 10, instead of the valve holder 20, the stubber surface portion 25 is omitted from the valve holder 20A of the embodiment shown in FIG. A cylindrical valve holder 20B having a lip piece 21A and an annular upper lip piece 23A at the upper end is provided. It is used. A hemispherical seat member (lower half) 60 is attached to the lower part of the valve holder 20B.

[0069] The base of the valve body 30 is constituted by a sphere 61, and the lower side of the sphere 61 is engaged with the hemispherical receiving seat member 60 so as to be displaceable in the axial direction. As a result, the valve body 30 is suspended and supported by the spherical joint type from the valve holder 20B.

[0070] The stagger portion for restricting the movement of the valve body side spring retainer material 35 to the lower lip piece 21A side of the valve holder 20B is constituted by the upper surface 62 of the hemispherical seat member 60. A hemispherical recess (upper half) 63 that receives the upper side of the sphere 61 is formed at the bottom of the valve-side spring retainer member 35.

In this embodiment as well, as in the first embodiment shown in FIG. 1, the lowermost position (shown in FIG. 10) in which the spherical body 61 of the valve body 30 closely engages with the hemispherical seat member 60. In the state where the valve body 30 is positioned and the lower bottom surface 35A of the valve body side spring retainer member 35 is in contact with the stopper surface 62, the valve body 30 and the valve body side spring retainer member 35 A gap tl is generated between the valve body side spring retainer member 35 and the valve body 30.

[0072] Therefore, also in this embodiment, it is possible to obtain the same effect as that of Embodiment 1 shown in Fig. 1, and that the valve body 30 is supported by being suspended from the valve holder 20B in a spherical joint type. Thus, the inclination of the valve body 30 is also automatically corrected, and the valve body 30 can always be seated on the valve seat surface portion 29 at an appropriate position. This makes it possible to obtain even better valve closing performance that does not cause fully closed leakage.

In the embodiment shown in FIG. 11, a cup-shaped lower lid member 99 is fixedly attached to the upper part of the valve housing 10, and the rotor case 71 is airtightly fixed to the upper part of the lower lid member 99. . The fixed support member 18 is fixedly attached to the lower lid member 99 by the mounting plate 17.

In this embodiment, since the valve seat surface portion 29 is a tapered surface, the valve body 90 is formed with a conical surface-shaped fully closed surface portion 31 at the root portion of the flow rate adjusting portion 33. When the fully closed surface portion 31 is seated on the valve seat surface portion 29, a fully closed state is obtained.

[0075] The valve body 90 has a valve stem portion 91 at a portion protruding from the valve holder 20C to the valve seat surface portion 29 side. In the valve housing 10, a sleeve-shaped stem guide member 98 is arranged so that a guide hole 97 formed in the stem guide member 98 is positioned concentrically with the valve port 12. Is attached. The valve stem portion 91 of the valve body 90 is fitted in the guide hole 97 of the stem guide member 98 so as to be displaceable in the axial direction. As a result, the valve stem portion 91 is guided and supported from the valve housing 10 via the stem guide member 98.

Even if the valve body 90 is separated from the male threaded shaft 73 by this guide support structure and the spring force of the compression coil spring 36 does not act on the valve body 90, the valve body 90 remains in the stem guide member.

98 is guided and supported, and the misalignment of the valve body 90 with respect to the valve port 12 is suppressed.

As a result, even if the valve body 90 rotates when the valve body 90 comes in contact with the valve seat surface portion 29, the fully closed surface portion 31 and the flow rate adjustment portion 33 of the valve body 90 are brought into contact with the valve seat surface portion 29. Rotating sliding wear caused by one piece is reduced.

[0078] Further, in a state where the center is shifted, the valve body 90 does not sit while rubbing the valve seat surface portion 29 (seal surface) under the action of the valve closing spring load!

[0079] Therefore, this guide support structure significantly exhibits the effect of preventing misalignment of the valve body 90 with respect to the valve port 12, and the reliability of the seal portion is further improved.

[0080] As in this embodiment, the stem guide member 98 is constituted by a separate part from the valve housing 10, so that the processing of the valve port 12 portion is facilitated and the space required for the valve chamber 11 is achieved. Can be easily secured. Further, since the stem guide member 98 is configured as a separate part from the valve housing 10, the valve housing 10 performs material selection as a structural part, and the stem guide member 98 individually selects material as a sliding member. Can be done. For example, the stem guide member 98 can be selected from copper alloy, sintered material, plastic, and the like.

[0081] Further, the upper end portion 76 of the male screw shaft 73 is fitted in a bearing hole 78A formed in the guide support shaft 78 so as to be rotatable and movable in the axial direction, and the upper end portion 76 of the male screw shaft 73 is guided. The bearing is supported by the support shaft 78.

Further, in this embodiment, as shown in FIG. 12, a lower end member 95 having an opening 101 is fixedly attached to the lower end portion of the valve holder 20C, and the lower end member 95 has a lower side surface portion. It is configured. A washer 94 and a cylindrical spacer member 93 are provided on the lower end member 95 in the valve holder 20C, and the upper end surface of the spacer member 93 is a stopper surface portion 25. The action of the stopper face portion 25 is the same as that of the stopper face portion 25 of the above-described embodiment. The valve body 90 passes through the opening 101 of the lower end member 95 in a loosely fitted state, and the upper end flange portion 92 is engaged with the washer 94, so that the valve body 90 can rotate from the valve holder 20C and in the axial direction. Suspended and supported to be displaceable.

Further, a screw shaft side spring retainer member 96 is disposed on the upper side in the valve holder 20C.

The compression coil spring 36 is provided between the screw shaft side spring retainer member 96 and the valve body side spring retainer member 35, and presses the screw shaft side spring retainer member 96 against the distal end surface of the male screw shaft 73. This spring mounting structure is substantially the same as the above-described embodiment, except for the presence or absence of the screw shaft side spring retainer member 96, as compared with the above-described embodiment.

As shown in FIG. 13 (a), the spacer member 93 may be integrally formed with the lower end member 95 as the spacer portion 93A. Further, as shown in FIG. 13 (b), a spacer portion 94A may be formed on the spacer member 93.

[0086] It should be noted that in these embodiments, the same operational effects as those of the first embodiment shown in FIG. 1 can be obtained.

(Embodiment 2 of electric control valve)

Embodiment 2 of the electric control valve according to the present invention will be described with reference to FIG. In FIG. 14, portions corresponding to those in FIG. 1 are denoted by the same reference numerals as those in FIG. 1, and description thereof is omitted.

[0088] A cylindrical valve holder 40 is provided in the guide hole 19 of the fixed support member 18 in the axial direction (vertical direction).

That is, they are slidably fitted in the valve opening / closing direction. As a result, the valve holder 40 can move in the axial direction in the valve housing 10. The valve holder 40 has an annular upper lip piece 41 having an upper side surface portion at the upper end.

A valve body 50 made of metal or synthetic resin is fixedly attached to the lower end portion of the valve holder 40. The valve body 50 has a flow rate adjusting portion (needle valve portion) 51 having a conical shape on the lower side.

[0090] The valve body 50 is a circle formed at the base of the flow rate adjusting unit 51 by performing quantitative flow rate control according to the degree of penetration (position in the axial direction) of the flow rate adjusting unit 51 with respect to the valve port 12. When the annular fully closed surface portion 52 is adhered to the valve seat surface portion 29 around the valve port 12, the valve port 12 is closed (closed) to be fully closed.

[0091] The valve holder 40 is provided with a lower end portion 74 of a male screw shaft 73 of the stepping motor 70. It penetrates the opening 42 inside the upper lip piece 41 of 0 in a loosely fitted state. The loose fitting state means that the valve holder 40 and the male screw shaft 73 can be relatively displaced in the radial direction.

[0092] At the lower end 74 of the male screw shaft 73, that is, at the front end of the male screw shaft 73, a flange-like hanging engagement portion is provided.

83 is formed. A spacer member 43 is provided on the upper side in the valve holder 40. The spacer member 43 is made of, for example, a material coated with a highly slippery plastic such as fluorine resin, or a highly slippery plastic, and has a cylindrical spacer part 43A.

And an annular washer portion 43B.

The suspension engagement portion 83 of the male screw shaft 73 is rotatably engaged with the upper lip piece 41 of the valve holder 40 with the spacer portion 43B of the spacer member 43 in the valve holder 40 interposed therebetween. By this engagement, the valve holder 40 is suspended and supported rotatably from the male screw shaft 73.

A screw shaft side spring retainer member 45 is provided in the valve holder 40 so as to be movable in the axial direction. The screw shaft side spring retainer member 45 is restricted from moving toward the upper lip piece 41 by the spacer portion 43A of the spacer member 43.

Due to this limitation, as shown in FIG. 14, when the suspended engaging portion 83 of the male screw shaft 73 is in contact with the washer portion 43B of the spacer member 43, the lower end portion of the male screw shaft 73 is provided. A gap t2 is generated between 74 and the screw shaft side spring retainer member 45, and the screw shaft side spring retainer member 45 and the male screw shaft 73 are separated.

A compression coil spring 46 is attached between the screw shaft side spring retainer member 45 and the valve body 50 in a state where a predetermined preload is applied.

The stepping motor 70 rotationally drives the male screw shaft 73 by the rotor 72, and linearly moves the valve holder 40 and the valve body 50 integrated therewith in the valve opening / closing direction by the axial movement of the male screw shaft 73 accompanying the rotation. .

[0098] As a result, the axial position of the flow rate adjusting portion 51 of the valve body 50 with respect to the valve port 12 (the linear movement position in the valve opening and closing direction) changes, and the effective opening area of the valve port 12 increases or decreases according to the axial position. Then, quantitative flow rate control is performed.

[0099] By the downward movement of the valve body 50 in the valve opening / closing direction, the effective opening area of the valve port 12 is gradually reduced, and the flow rate of the fluid flowing through the valve port 12 is gradually reduced accordingly. When the valve body 50 moves downward by a predetermined amount in the valve opening / closing direction, the fully closed surface 52 of the valve body 50 is in contact with the valve seat surface 29. By sitting, the valve port 12 is fully closed.

[0100] Next, the operation of the electric control valve according to Embodiment 2 will be described in detail with reference to FIGS.

FIG. 19 (a) shows the relationship between the number of pulses of the stepping motor 70 and the axial displacement of the male screw shaft 73 and the valve holder 40 and the valve body 50 in this embodiment, and FIG. 19 (b) shows the stepping motor 70. FIG. 19 (c) shows the relationship between the number of pulses of the stepping motor 70 and the flow rate. FIG. 19 (c) shows the relationship between the number of pulses and the spring load (valve closing spring load pressing the valve body 40 against the valve seat 29). In FIG. 19 (a), L73 indicates the displacement of the male screw shaft 73, and L40 & 50 indicates the displacement of the valve holder 40 and the valve body 50, respectively. 19 (a) to (c), (1) shows the operating state of FIG. 15, (2) shows the operating state of FIG. 16, (3) and (4) shows the operating state of FIG. (5) shows the operation states of Fig. 18 respectively.

FIG. 15 shows a valve open state (control region) in which the fully closed surface portion 52 of the valve body 50 is separated from the valve seat surface portion 29. In this valve open state, the suspension engaging portion 83 of the male screw shaft 73 engages with the upper lip piece 41 of the valve holder 40 with the spacer portion 43B of the spacer member 43 interposed therebetween, and the valve holder 40 and the valve holder 40 The integral valve body 50 is suspended from the male screw shaft 73! /.

[0103] When the valve is in the open state, the screw shaft side spring retainer member 45 abuts on the spacer 43A of the spacer member 43, and the action of the spacer member 43 causes the screw shaft side spring retainer member 45 to move to the male screw shaft. A gap t2 exists between the male screw shaft 73 and the screw shaft side spring retainer member 45 and is spaced from the tip 74 of the 73.

Thus, in the valve open state, the male threaded shaft 73 and the threaded shaft side spring retainer member 45 are separated from each other, and the valve element 50 serves as a valve closing spring load in which the spring force of the compression coil spring 46 is effective on the male threaded shaft 73. The spring force of the compression coil spring 46 acts between the valve body 50 and the valve holder 40 integrated therewith, and the spring load of the compression coil spring 46 is fully within the valve holder 40. The spring force of the compression coil spring 46 does not act on the valve body 50 as an effective valve closing spring load (state (1) in FIG. 19). Under this condition, the valve holder 40 and the valve body 50 can freely rotate relative to the male screw shaft 73.

[0105] In the control region, the male screw shaft 73 rotates while being disconnected from the valve holder 40 and the valve body 50, so that friction loss is reduced and the electric power of the stepping motor 70 necessary for the flow control operation is reduced. Power can be reduced.

From this valve open state, the male screw shaft 73 is driven to rotate in the valve closing direction by the stepping motor 70, so that the male screw shaft 73, the valve holder 40, and the valve body 50 all move downward. Due to this lowering, as shown in FIG. 16, the fully closed surface portion 52 of the valve body 50 is seated on the valve seat surface portion 29 (state (2) in FIG. 19).

[0107] At the moment when the fully closed surface portion 52 of the valve body 50 is seated on the valve seat surface portion 29, a gap t2 continues to exist between the male screw shaft 73 and the screw shaft side spring retainer member 45, and the spring of the compression coil spring 46 Since the force does not act on the valve holder 40 and the valve body 50 as an effective valve-closing spring load, the valve body 50 is fully closed even if the valve holder 40 and the valve body 50 are rotated by the rotation of the male screw shaft 73. When the surface 52 is seated on the valve seat surface 29, the valve holder 40 and the valve body 50 rotate due to friction of the valve holder 40 and the valve body 50 due to the contact between the fully closed surface 52 and the valve seat surface 29. No longer

That is, the fully closed surface portion 52 of the valve body 50 is seated without sliding around the valve seat surface portion 29.

[0109] At this time, even if the fully closed surface portion 52 of the valve body 50 rotates with respect to the valve seat surface portion 29, only a frictional resistance corresponding to the weight of the valve holder 40 and the valve body 50 is generated. The contact surface between the fully closed surface portion 52 and the valve seat surface portion 29 of the valve body 50 does not cause large wear.

[0110] Further, since the spring force of the compression coil spring 46 is not applied to the valve holder 40 and the valve body 50 as an effective valve closing spring load, the valve holder 40 and the valve body 50 are externally threaded when the valve is opened to seated. Even if the male threaded shaft 73 and the valve seat surface portion 29 (valve port 12) are misaligned, the valve body 50 can be displaced while the fully closed surface portion 52 is in one-piece contact. The contact with the seat 29 is no longer possible, and the valve body 50 is always seated on the valve seat 29 in an appropriate position and posture.

[0111] If the male screw shaft 73 is driven to rotate in the valve closing direction by the stepping motor 70 from the state in which the fully closed surface portion 52 of the valve body 50 is seated on the valve seat surface portion 29, the fully closed surface portion of the valve body 50 The male screw shaft 73 moves downward while 52 is seated on the valve seat 29.

[0112] By this downward movement, the gap between the male screw shaft 73 and the screw shaft side spring retainer member 45 is narrowed, and the movement of the male screw shaft 73 in the valve closing direction causes the fully closed surface portion 52 of the valve body 50 to move to the valve. The male screw shaft 73 is positioned relative to the valve holder 40 relative to the valve holder 40 when seated on the seat surface 29. When moved to the side by a predetermined value or more, as shown in FIG. 17, the lower end portion 74 of the male screw shaft 73 comes into contact with the screw shaft side spring retainer member 45 (state (3) in FIG. 19).

[0113] Until the moment when the lower end portion 74 of the male screw shaft 73 contacts the screw shaft side spring retainer member 45, the spring force of the compression coil spring 46 does not act on the valve body 50 as an effective valve closing spring load. The fully closed surface portion 52 of the valve body 50 does not slide against the valve seat surface portion 29 under the action of the valve spring load of the compression coil spring 46.

[0114] At the moment when the lower end 74 of the male screw shaft 73 contacts the screw shaft side spring retainer member 45, the spring force of the compression coil spring 46 acts on the valve holder 40 and the valve body 50 as an effective valve closing spring load. However, the fully closed surface 52 of the valve body 50 is pressed against the valve seat surface 29 by the spring force of the compression coil spring 46, where a valve closing spring load is generated and the valve closing performance is improved. can get

[0115] Thus, after the fully closed surface portion 52 of the valve body 50 is seated on the valve seat surface portion 29, the spring force of the compression coil spring 46 acts on the valve holder 40 and the valve body 50 as an effective valve spring load. Therefore, the fully closed surface portion 52 of the valve body 50 may slide with a large frictional force against the valve seat surface portion 29 while being pressed against the valve seat surface portion 29 by the spring force of the compression coil spring 46. Absent

[0116] When the fully closed surface portion 52 of the valve body 50 is separated from the valve seat surface portion 29 in the valve opening process, similarly, the valve body 50 is pressed against the valve seat surface portion 29 by the spring force of the compression coil spring 46. Therefore, the frictional resistance corresponding to the weight of the valve holder 40 and the valve body 50, which prevents the fully closed surface portion 52 of the valve body 50 from sliding around the valve seat surface portion 29, is generated. Wear on the contact surface between the valve seat surface portion 29 and the valve seat surface portion 29 is reduced.

That is, the frictional force generated between the valve body 30 and the valve seat surface portion 29 at the moment when the fully closed surface portion 52 of the valve body 50 is seated on and separated from the valve seat surface portion 29 is The amount of wear is extremely small even when the valve body 50 is operated by repeated weight.

[0118] Because of these, even if repeated operating conditions are required, the contact surface between the fully closed surface portion 52 and the valve seat surface portion 29 of the valve body 50 is not subjected to violent wear, and the fully closed leakage over a long period of time. Excellent valve closing performance can be obtained.

[0119] Further, as described above, the fully closed surface portion 52 of the valve body 50 is in contact with the valve seat surface portion 29 in a single-contact state. Since the valve body 50 that cannot be touched always sits on the valve seat surface portion 29 in an appropriate position and posture, this also provides an excellent valve closing performance that does not cause a fully closed leak.

When the male screw shaft 73 is further rotated in the valve closing direction by the stepping motor 70, the screw shaft side spring retainer is moved by the lower end portion 74 of the male screw shaft 73 as shown in FIG. The member 45 is pushed downward, and the state in which the spring force of the compression coil spring 46 acts on the valve holder 40 and the valve body 50 as an effective valve spring load continues, and the reference point is found in the fully closed state (FIG. 19). (State of (5)).

[0121] (Modification of Embodiment 2)

A modification (another embodiment) of the electric control valve according to the second embodiment will be described with reference to FIGS. In FIGS. 20 and 21, portions corresponding to those in FIGS. 1, 11, and 14 are denoted by the same reference numerals as those in FIGS. 1, 11, and 14, and description thereof is omitted.

In the embodiment shown in FIG. 20, an upper hemispherical seat member (upper half body) 64 is provided as a spacer member on the upper portion of the valve holder 40. The lower end portion 74 of the male screw shaft 73 is a sphere 65 that forms a suspended engagement portion, and the sphere 65 is engaged with the hemispherical seat member 64 so as to be displaceable in the axial direction.

Accordingly, the valve holder 40 is supported by being suspended from the male screw shaft 73 in a spherical joint type.

[0124] Further, a hemispherical recess (lower half) 66 for receiving the lower side of the sphere 65 is formed on the upper part of the screw shaft side spring retainer member 45.

In this embodiment as well, as in the second embodiment shown in FIG. 14, the screw shaft side spring retainer member 45 is moved to the upper lip piece 41 side by the hemispherical seat member 64 that forms the spacer member. When the spherical body 65 of the male screw shaft 73 is closely engaged with the hemispherical seat member 64 (the state shown in FIG. 20), the spherical body 65 and the screw shaft side spring retainer member are restricted. A gap t2 is generated between the screw shaft side 45 and the screw shaft side spring retainer member 45 and the male screw shaft 73 are separated.

[0126] Therefore, in this embodiment, the same effect as that of Embodiment 2 shown in Fig. 14 can be obtained, and the force of the valve holder 40 and valve body 50 is suspended from the male screw shaft 73 in a spherical joint type. By being supported, the inclination of the valve holder 40 and the valve body 50 is also automatically corrected, so that the valve body 50 is always suitable. It becomes possible to seat on the valve seat surface portion 29 at the optimal position, and excellent valve closing performance can be obtained without causing full-closed leakage.

In the embodiment shown in FIG. 21, the valve holder 40A is supported in the guide hole 19 of the stationary support member 18 of the electric control valve shown in FIG. 11, and the valve holder 40A is shown in FIG. A configuration similar to the inside of the valve holder 40 of the electric control valve is provided, and the valve body 90 is fixedly attached to the lower end of the valve holder 40A. A sleeve-shaped stem guide member 98 is attached to the valve housing 10 so that the guide hole 97 is positioned concentrically with the valve port 12, and the valve stem portion 91 of the valve body 90 is attached to the stem guide member 98. The guide hole 97 is fitted so as to be displaceable in the axial direction. As a result, the valve stem portion 91 is guided and supported from the valve housing 10 via the stem guide member 98, as in the embodiment shown in FIG.

[0128] With this guide support structure, the valve body 90 is separated from the male screw shaft 73, and the spring force of the compression coil spring 46 does not effectively act on the valve body 90. The guide member 98 guides and supports the displacement of the valve body 90 relative to the valve port 12.

As a result, even when the valve body 90 rotates when the valve body 90 comes into contact with the valve seat surface portion 29, the fully closed surface portion 31 and the flow rate adjustment portion 33 of the valve body 90 are brought into contact with the valve seat surface portion 29. Rotating sliding wear caused by one piece is reduced.

[0130] In addition, the valve body 90 may be seated while rubbing the valve seat surface portion 29 (seal surface) under the load of the valve closing spring in a state where the center is shifted!

[0131] Therefore, this guide support structure significantly exerts the effect of preventing the misalignment of the valve body 90 with respect to the valve port 12, and the reliability of the seal portion is further improved.

[0132] Also in this embodiment, the stem guide member 98 is constituted by a separate part from the valve housing 10, so that the processing of the valve port 12 portion is facilitated, and the space necessary for the valve chamber 11 is facilitated. Can be secured. Further, since the stem guide member 98 is configured as a separate component from the valve housing 10, the valve housing 10 performs material selection as a structural component, and the stem guide member 98 individually selects material as a sliding member. Can be performed. [0133] Note that, in this embodiment as well, the same operational effects as those of Embodiment 2 shown in Fig. 14 can be obtained.

[Embodiment 3 of Electric Control Valve]

Embodiment 3 of the electric control valve according to the present invention will be described with reference to FIG. Note that in FIG. 22, the same reference numerals as those shown in FIGS. 1, 11, and 14 are used for the description corresponding to FIGS. 1, 11, and 14. Omitted.

In the embodiment shown in FIG. 22, the lower end member 95 is fixedly attached to the lower end portion of the valve holder 40Α, and the lower end member 95 constitutes the lower side surface portion. The valve body 90 passes through the opening 101 of the lower end member 95 in a loosely fitted state, and the upper end flange portion 92 abuts against the lower end member 95, so that the valve body 90 can be rotated from the valve holder 40Α and can be displaced in the axial direction. It is supported by lowering.

In this embodiment, as shown in FIG. 23, a cylindrical spacer member 47 and an annular high slipper washer member 48 are provided on the upper side in the valve holder 40. .

[0137] The suspension engagement portion 83 of the male screw shaft 73 is rotatably engaged with the upper lip piece 41 of the valve holder 40Α with the high slipper washer member 48 in the valve holder 40Α interposed therebetween. By this engagement, the valve holder 40Α is suspended and supported rotatably from the male screw shaft 73.

[0138] A screw shaft side spring retainer member 45 is provided in the valve holder 40Α so as to be movable in the axial direction. The screw shaft side spring retainer member 45 is restricted from moving toward the upper lip piece 41 by the spacer member 47. As well shown in FIG. 24, the axial length Β of the spacer member 47 is longer than the axial length 係合 of the engaging portion with respect to the valve holder 40 Α including the suspended engaging portion 83 at the tip of the male screw shaft 73. Is set to Therefore, also in this embodiment, a gap t2 is generated between the lower end portion 74 of the male screw shaft 73 and the screw shaft side spring retainer member 45, and the screw shaft side spring retainer member 45 and the male screw shaft 73 are separated.

[0139] A compression coil spring 46 is attached between the screw shaft side spring retainer member 45 and the upper end flange portion 92 of the valve body 90 in a state where a predetermined preload is applied.

[0140] The valve body 90 has a valve stem portion 91 at a portion protruding from the valve holder 40A to the valve seat surface portion 29 side. In the valve housing 10, a sleeve-shaped stem guide member 98 is arranged so that a guide hole 97 formed in the stem guide member 98 is positioned concentrically with the valve port 12. Is attached. The valve stem portion 91 of the valve body 90 is fitted in the guide hole 97 of the stem guide member 98 so as to be displaceable in the axial direction. As a result, the valve stem portion 91 is guided and supported from the valve housing 10 via the stem guide member 98.

[0141] A pressure equalizing spiral groove 106 is formed in the stem guide member mounting portion of the valve housing 10. The pressure equalizing spiral groove 106 is formed on the outer peripheral surface of the stem guide member 98 of the valve body 90.

[0142] Next, the operation of the electric control valve according to the third embodiment will be described in detail with reference to Figs.

FIG. 29 (a) shows the relationship between the number of pulses of the stepping motor 70 and the axial displacement of the male screw shaft 73 and the valve holder 40A and the valve body 90 in this embodiment. FIG. 29 (b) shows the stepping motor 70. FIG. 29 (c) shows the relationship between the number of pulses and the spring load (valve closing spring load that presses the valve body 90 against the valve seat 29), and FIG. 29 (c) shows the relationship between the number of pulses of the stepping motor 70 and the flow rate. In FIG. 29 (a), L73 indicates the displacement of the male screw shaft 73, L40A indicates the displacement of the valve holder 40A, and L90 indicates the displacement of the valve body 90. In Figs. 29 (a) to (c), (1) shows the operating state of Fig. 25, (2) shows the operating state of Fig. 26, and (3) and (4) show the operating state of Fig. 27. (5) shows the operation states of FIG. 28, respectively.

FIG. 25 shows a valve open state (control region) in which the flow rate control unit 33 of the valve body 90 is separated from the valve seat surface portion 29. In this valve open state, the suspension engaging portion 83 of the male screw shaft 73 is engaged with the upper lip piece 41 of the valve holder 40A with the high slipper washer 48 interposed therebetween, and the valve holder 40A and the valve body 90 are connected to the male screw shaft 73. It is more suspended.

[0145] When the valve is in the open state, the screw shaft side spring retainer member 45 contacts the spacer member 47, and the action of the spacer member 47 causes the screw shaft side spring retainer member 45 to move from the tip end portion 74 of the male screw shaft 73. A gap t2 exists between the male screw shaft 73 and the screw shaft side spring retainer member 45.

Thus, in the valve open state, the male screw shaft 73 and the screw shaft side spring retainer member 45 are separated from each other, and the valve element 90 is used as a valve closing spring load in which the spring force of the compression coil spring 46 is effective on the male screw shaft 73. The compression coil spring 46 acts between the valve body 90 and the valve holder 40A integral with the valve body 90, and the spring load of the compression coil spring 46 is completed within the valve holder 40A. The spring force of the oil spring 46 does not act on the valve body 90 as an effective valve closing spring load (state (1) in FIG. 29). Under this state, the valve holder 40A and the valve body 90 can freely rotate relative to the male screw shaft 73.

[0147] In the control region, the male screw shaft 73 rotates while being disconnected from the valve holder 40A and the valve body 90, so that the friction loss is reduced and the power of the stepping motor 70 required for the flow control operation can be reduced.

[0148] From this valve open state, the male screw shaft 73 is driven to rotate in the valve closing direction by the stepping motor 70, whereby the male screw shaft 73, the valve holder 40A, and the valve body 90 all move down. Due to this lowering, as shown in FIG. 26, the fully closed surface portion 31 of the valve body 90 is seated on the valve seat surface portion 29 (state (2) in FIG. 29).

[0149] At the moment when the fully closed surface portion 31 of the valve body 90 is seated on the valve seat surface portion 29, a gap t2 continues to exist between the male screw shaft 73 and the screw shaft side spring retainer member 45, and the spring of the compression coil spring 46 Since the force does not act on the valve holder 40A and the valve body 90 as an effective valve closing spring load, the valve body 90 can be fully closed even if the valve holder 40A and the valve body 90 are rotated by the rotation of the male screw shaft 73. When the surface portion 31 is seated on the valve seat surface portion 29, the valve holder 40A and the valve body 90 rotate due to friction of the valve holder 40A and the valve body 90 due to the contact between the fully closed surface portion 31 and the valve seat surface portion 29. No longer.

That is, the fully closed surface portion 31 of the valve body 90 is seated without sliding around the valve seat surface portion 29.

[0151] At this time, even if the fully closed surface portion 31 of the valve body 90 rotates with respect to the valve seat surface portion 29, only a frictional resistance corresponding to the weight of the valve holder 40A and the valve body 90 is generated. The contact surface between the fully closed surface portion 31 and the valve seat surface portion 29 of the valve body 90 is not large and worn.

[0152] Also, since the spring force of the compression coil spring 46 is not effective against the valve holder 40A and the valve body 90 as a closed valve load, the valve holder 40A and the valve body 90 are Therefore, even if the male screw shaft 73 and the valve seat surface portion 29 (valve port 12) are misaligned, the fully closed surface portion 31 of the valve element 90 is in a single contact state. As a result, the valve seat 90 is not touched and the valve element 90 is always seated on the valve seat 29 in an appropriate position and posture.

[0153] From the state in which the fully closed surface 31 of the valve body 90 is seated on the valve seat surface 29, the stepping mode is further increased. When the male screw shaft 73 is rotationally driven in the valve closing direction by the rotor 70, the male screw shaft 73 moves downward while the fully closed surface portion 31 of the valve body 90 is seated on the valve seat surface portion 29.

[0154] By this downward movement, the gap between the male screw shaft 73 and the screw shaft side spring retainer member 45 is narrowed, and the movement of the male screw shaft 73 in the valve closing direction causes the fully closed surface portion 31 of the valve element 90 to move to the valve. When the male threaded shaft 73 moves relative to the valve holder 40A relative to the valve holder 40A by a predetermined value or more from the seated surface 29, the lower end of the male threaded shaft 73 as shown in FIG. 74 comes into contact with the screw shaft side spring retainer member 45 (state (3) in FIG. 29).

[0155] Until the moment when the lower end 74 of the male screw shaft 73 contacts the screw shaft side spring retainer member 45, the spring force of the compression coil spring 46 does not act on the valve body 90 as an effective valve closing spring load. The fully closed surface portion 31 of the valve body 90 does not slide against the valve seat surface portion 29 under the action of the valve spring load of the compression coil spring 46.

[0156] At the moment when the lower end 74 of the male screw shaft 73 contacts the screw shaft side spring retainer member 45, the spring force of the compression coil spring 46 acts on the valve body 90 as an effective valve closing spring load (Fig. 29). (State (4)), the fully closed surface portion 31 of the valve body 90 is pressed against the valve seat surface portion 29 by the spring force of the compression coil spring 46, where a valve closing spring load is generated and the valve closing performance is obtained.

[0157] Thus, after the fully closed surface portion 31 of the valve body 90 is seated on the valve seat surface portion 29, the spring force of the compression coil spring 46 acts on the valve body 90 as an effective valve closing spring load. The 90 fully closed surface portions 31 are pressed against the valve seat surface portion 29 by the spring force of the compression coil spring 46, so that they cannot slide over the valve seat surface portion 29 with a large frictional force!

[0158] When the fully closed surface portion 31 of the valve body 90 is separated from the valve seat surface portion 29 in the valve opening process, similarly, the valve body 90 is pressed against the valve seat surface portion 29 by the spring force of the compression coil spring 46. In this case, only the frictional resistance of the valve holder 90 and its own weight is generated, so that the fully closed surface portion 31 of the valve body 90 does not slide around the valve seat surface portion 29. Wear on the contact surface between the valve seat surface portion 29 and the valve seat surface portion 29 is reduced.

That is, the frictional force generated between the valve body 90 and the valve seat surface portion 29 at the moment when the fully closed surface portion 31 of the valve body 90 is seated on and separated from the valve seat surface portion 29 is This is due to the weight of the valve body 90 only, and the amount of wear is extremely small even if it is repeatedly operated.

[0160] Because of these, even if repeated operating conditions are required, Excellent valve closing performance can be obtained without causing full-closed leakage over a long period of time, in which the contact surface with the valve seat portion 29 does not wear severely.

[0161] In addition, as described above, the valve body 90 in which the fully closed surface portion 31 of the valve body 90 does not come into contact with the valve seat surface portion 29 in a single contact state is always in an appropriate position and posture. Therefore, it is possible to obtain an excellent valve closing performance that does not cause a fully closed leak.

When the male screw shaft 73 is further rotated in the valve closing direction by the stepping motor 70, the screw shaft side spring retainer is moved by the lower end portion 74 of the male screw shaft 73 as shown in FIG. The state where the member 45 is pushed downward and the spring force of the compression coil spring 46 acts on the valve body 90 as an effective valve closing spring load continues, and the reference point is found in the fully closed state ((5) in Fig. 29). State).

[0163] In this state, an axial gap t3 is formed between the upper end flange portion 92 and the lower end member 95 of the valve body 90, and the valve holder 40A, the spacer member 47, and the highly slippery washer member 48 are formed. Is in a state of only being on the screw shaft side spring retainer member 45.

[0164] In this embodiment, the valve body 90 only rides on the male screw shaft 73 by its own weight. Therefore, when the valve body 90 contacts the valve seat surface portion 29, the valve body 90 and the male screw shaft 73 are connected. It is cut off and no torque is transmitted to the valve seat 29. This is also the case when foreign matter is swallowed into the valve seat surface 29.The valve body 90 seated on the foreign matter stops moving there, and then a static axial load is applied by the spring load. Force Since it is not a load while sliding, the possibility that the valve seat 29 will be damaged is extremely low. The structure of the present embodiment is effective not only for improving the wear resistance of the valve seat surface portion 29 but also for trapping foreign matter in the fluid.

[0165] Also in this embodiment, in the control region, the male screw shaft 73 rotates in a state of being disconnected from the valve body 90, so that the friction loss is reduced and the stepping motor 70 necessary for the flow rate control operation is reduced. Electric power can be reduced.

In this embodiment, since the valve stem portion 91 is guided and supported by the valve housing 10 via the stem guide member 98, the valve body 90 is separated from the male screw shaft 73, and the compression coil spring 46 is Even when the spring force is not effectively applied to the valve body 90, the valve body 90 is guided and supported by the system guide member 98 even in the free state, and the center displacement of the valve body 90 with respect to the valve port 12 is suppressed. Be controlled.

[0167] As a result, even when the valve body 90 rotates when the valve body 90 moves away from the valve seat surface portion 29, the fully closed surface portion 31 and the flow rate adjustment portion 33 of the valve body 90 are brought into contact with the valve seat surface portion 29. Rotating sliding wear caused by one piece is reduced.

[0168] In addition, the valve body 90 may be seated while rubbing the valve seat surface portion 29 (seal surface) under the load of the valve closing spring in a state where the center is shifted!

[0169] Therefore, this guide support structure significantly exerts the effect of preventing misalignment of the valve body 90 with respect to the valve port 12, and the reliability of the seal portion is further improved.

Further, as shown in FIG. 30, even if the male screw shaft 73 is inclined at an inclination angle Θ, the valve holder 40A is lifted by the tip of the male screw shaft 73! Since the load in the radial direction is difficult to be applied due to the inclination of the tilt, it is difficult for large friction loss to occur.

[0171] (Modification of Embodiment 3)

A modification (another embodiment) of the electric control valve according to Embodiment 3 will be described with reference to FIGS. In addition, Fig. 31 and Fig. 32 [Koo !, Fig. 1, Fig. 22, Fig. 23] Corresponding parts are given the same reference numerals as those shown in Fig. 1, Fig. 22, and Fig. 23. The explanation is omitted.

[0172] In the embodiment shown in Fig. 31, the high slipper washer 102 is provided between the upper end flange portion 92 and the lower end member 95 of the valve body 90, and the operability can be further improved.

In the embodiment shown in FIG. 32, the stem guide hole 97 is directly formed in the valve housing 10 to reduce the number of parts.

Industrial applicability

[0174] The electric control valve according to the present invention can be used as an expansion valve of a refrigeration cycle apparatus!

Claims

The scope of the claims

[1] A male screw portion formed on a male screw shaft that is rotationally driven by a rotor of a stepping motor is screwed into a female screw hole of a female screw member fixed to the valve housing, and the male screw shaft is moved in the axial direction by the screw engagement. In the electric control valve which opens and closes the valve body by moving the male screw shaft in the axial direction and fully closes the valve port by seating the valve body on the valve seat provided in the valve housing.

The male screw shaft and the valve body are connected to each other so as to be relatively displaceable in the axial direction by a cylindrical valve holder disposed in the valve housing so as to be movable in the axial direction, and the valve body is connected to the valve seat portion. When seated, no spring load is generated to press the valve body against the valve seat portion, and when the male screw shaft is further moved a predetermined amount or more in the valve closing direction, a spring load is applied to press the valve body against the valve seat portion. An electric control valve characterized in that a compression spring is incorporated in the valve holder so as to occur.

[2] The male screw portion formed on the male screw shaft that is rotationally driven by the rotor of the stepping motor is screwed into the female screw hole of the female screw member fixed to the valve housing, and the male screw shaft moves in the axial direction by the screw engagement. In the electric control valve which opens and closes the valve body by moving the male screw shaft in the axial direction and fully closes the valve port by seating the valve body on the valve seat provided in the valve housing.

A cylindrical valve holder is disposed in the valve housing so as to be movable in the axial direction. The valve body is attached to the valve holder so as to be displaceable in the axial direction, and is formed at one end of the valve holder. When the valve body is engaged with the lower surface portion formed, the valve body is supported by being suspended from the valve holder,

A suspension engaging portion formed at the tip of the male screw shaft engages with an upper side surface formed at the other end of the valve holder, so that the valve holder is suspended and supported from the male screw shaft. ,

A valve body side spring retainer member is provided in the valve holder so as to be movable in the axial direction in a state where movement to the lower side surface side is restricted by abutting against a strobe portion provided in the valve holder,

Compressed between the hanging engagement portion of the male screw shaft and the valve body side spring retainer member Ne is attached,

The valve holder is relative to the valve body when the valve body is separated from the valve seat portion and when the valve body is seated on the valve seat portion due to movement of the male screw shaft in the valve closing direction. The valve body side spring retainer member abuts against the stopper portion and is separated from the valve body until the valve seat side moves to a predetermined value or more, and the valve body side spring retainer member and the valve body are separated. From the state in which the spring force of the compression spring does not act on the valve body, and the valve body is seated on the valve seat portion by the valve closing direction movement of the male screw shaft, the valve is moved by the valve closing direction movement of the male screw shaft. In a state where the holder has moved relative to the valve body toward the valve seat portion by a predetermined value or more, the valve body side spring retainer member is in contact with the valve body in a state of being separated from the strobe portion, and the compression is performed. The spring force of the spring is applied to the valve body It is given,

This is an electric control valve.

The male screw portion formed on the male screw shaft rotated by the rotor of the stepping motor is screwed into the female screw hole of the female screw member fixed to the valve housing, and the male screw shaft moves in the axial direction by the screw engagement, and the In the electric control valve that fully closes the valve port by driving the valve body to open and close by moving the male screw shaft in the axial direction and seating the valve body on the valve seat provided in the valve housing,

A cylindrical valve holder disposed in the valve housing so as to be movable in the axial direction; the valve body is fixedly attached to one end of the valve holder;

A screw shaft side spring retainer member is provided in the valve holder so as to be movable in the axial direction in a state where movement to the upper side surface portion side is restricted by a spacer member provided in the valve holder. ,

A compression spring is attached between the screw shaft side spring retainer member and the valve body,

The valve body is separated from the valve seat portion and the male screw shaft moves in the valve closing direction. Therefore, the operation of the spacer member until the male screw shaft moves more than a predetermined value relative to the valve holder from the state where the valve body is seated on the valve seat portion to the valve seat portion side. When the tip of the male screw shaft is separated from the screw shaft side spring retainer member, the spring force of the compression spring does not act as a valve closing spring load on the valve holder and the valve body,

In a state in which the male screw shaft is moved more than a predetermined value relative to the valve holder by the valve closing direction movement of the male screw shaft from the state where the valve body is seated on the valve seat portion. The tip of the male screw shaft abuts on the screw shaft side spring retainer member to apply the spring force of the compression spring to the valve body.

This is an electric control valve.

A suspension engagement portion formed at the tip of the male screw shaft engages with an upper side surface formed at the other end of the valve holder, whereby the valve holder is suspended from the male screw shaft so as to be rotatable. Supported,

The valve body is separated from the valve seat portion and the male screw shaft moves in the valve closing direction. Therefore, from the state where the valve body is seated on the valve seat portion, until the male screw shaft moves more than a predetermined value relative to the valve body toward the valve seat portion, the action of the spacer member Since the tip of the male screw shaft does not press the screw shaft side spring retainer member, the spring force of the compression spring does not act as a valve closing spring load on the valve body, and the valve body acts on the valve seat portion. When the male screw shaft moves relative to the valve body toward the valve seat portion by a predetermined value or more by the movement of the male screw shaft in the valve closing direction from the seated state, the tip of the male screw shaft is the screw shaft. Abutting on a side spring retainer member to apply a spring force of the compression spring to the valve body;

This is an electric control valve.

5. The electric control valve according to any one of claims 1, 2, and 4, wherein the valve body is provided so as to be displaceable in a radial direction with respect to the valve holder.

6. The electric control valve according to any one of claims 1 to 5, wherein the male screw shaft and the valve holder are provided so as to be displaceable in a radial direction.

[7] The valve body has a valve stem portion at a portion protruding from the valve holder toward the valve seat portion, and the valve stem portion is changed in an axial direction to a stem guide portion provided in the valve housing. The electric control valve according to any one of claims 1 to 6, wherein the electric valve is fitted so as to be able to be moved and the valve stem portion is guided and supported by the valve housing.