JP2022188975A - electric valve - Google Patents

Abstract

To provide an electric valve which can further reduce noise while keeping cost low.SOLUTION: An electric valve includes: valve main body having a valve chamber; a valve seat member attached to the valve main body and having a valve seat; and a valve body arranged in the valve chamber and movable up and down in a direction in which the valve body approaches or separates from the valve seat. The valve seat member includes an orifice part connectable to piping and adjacent to the valve seat, and a rectification hole continuous with the orifice part. A center axis of the rectification hole intersects with an inner wall of the piping.SELECTED DRAWING: Figure 2

Description

The present invention relates to an electrically operated valve.

A motor-operated valve used as a flow control valve in a refrigeration cycle has a screw mechanism in which a male screw portion of a valve shaft rotated by a motor is screwed into a female screw hole provided in a valve body. By converting rotary motion into axial motion, the valve stem is axially displaced to control the flow rate.

For example, Patent Literature 1 discloses a motor-operated valve in which a thin plate member (punching plate) having a large number of small holes that exhibit a throttling function and a bubble segmentation function is attached to a main body and allows a refrigerant to pass through. According to such a thin plate member, the function of rectifying the refrigerant passing in the two-phase flow state, the function of throttling, and the function of dividing the air bubbles in the refrigerant in the two-phase flow state are exhibited, and the refrigerant passage noise caused by the air bubbles can be effectively reduced. can be reduced to

JP 2007-107623 A

In the refrigerating cycle, since the refrigerant generally flows into the valve main body of the motor-operated valve from the pipe in a gas-liquid two-phase flow state, it inherently contains air bubbles. Also, when the refrigerant passes through the orifice, a pressure drop occurs, and a part of the refrigerant vaporizes to generate bubbles. Noise is generated when such bubbles burst.

According to the motor-operated valve of Patent Document 1, it is possible to reduce the refrigerant passage noise caused by air bubbles, but there is still room for further quieting.

The present inventors found that in the motor-operated valve of Patent Document 1, when the refrigerant that has passed through the orifice passes through the small holes of the thin plate member in the process of pressure recovery and enters a larger diameter pipe, turbulence occurs. It was found that noise was generated by generating. Moreover, since the motor-operated valve of Patent Document 1 requires a thin plate member, there is also the problem that the number of parts increases and assembly takes time and effort.

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide an electrically operated valve that can further reduce noise while suppressing costs.

In order to solve the above problems, the motor operated valve of the present invention includes:
a valve body having a valve chamber;
a valve seat member attached to the valve body and having a valve seat;
a valve body arranged in the valve chamber and capable of moving up and down in a direction toward or away from the valve seat;
The valve seat member is connectable to a pipe and includes an orifice portion adjacent to the valve seat and a rectifying hole connected to the orifice portion,
A central axis of the rectifying hole intersects an inner wall of the pipe.

According to the present invention, it is possible to provide an electrically operated valve that can further reduce noise while suppressing costs.

FIG. 1 is a longitudinal sectional view showing an electrically operated valve according to a first embodiment of the invention. FIG. 2 is a longitudinal sectional view of the valve seat member according to the first embodiment. FIG. 3 is a bottom perspective view of the valve seat member according to the first embodiment. FIG. 4 is a bottom view of the valve seat member according to the first embodiment. FIG. 5 is a vertical cross-sectional view of a valve seat member that can be used in the electrically operated valve according to the second embodiment. FIG. 6 is a vertical cross-sectional view of a valve seat member that can be used in the electrically operated valve according to the third embodiment. FIG. 7 is a vertical cross-sectional view of a valve seat member that can be used in the electric valve according to the fourth embodiment. FIG. 8 is a vertical cross-sectional view of a valve seat member that can be used in the electric valve according to the fifth embodiment. FIG. 9 is a vertical cross-sectional view of a valve seat member that can be used in the electric valve according to the sixth embodiment. FIG. 10 is a vertical cross-sectional view of a valve seat member that can be used in the electrically operated valve according to the seventh embodiment. FIG. 11 is a vertical cross-sectional view of a valve seat member that can be used in the electric valve according to the eighth embodiment. FIG. 12 is a vertical cross-sectional view of a valve seat member that can be used in the electrically operated valve according to the ninth embodiment. FIG. 13 is a vertical cross-sectional view of a valve seat member that can be used in the electric valve according to the tenth embodiment. FIG. 14 is a vertical cross-sectional view of a valve seat member that can be used in the electrically operated valve according to the eleventh embodiment. FIG. 15 is a diagram showing a configuration in which a valve seat member and a porous filter that can be used in an electrically operated valve according to a modification of the present embodiment are combined.

Hereinafter, embodiments according to the present invention will be described with reference to the drawings.

[First Embodiment]
FIG. 1 is a longitudinal sectional view showing an electrically operated valve 1 according to a first embodiment of the invention. Here, the rotor side of the electric valve 1 is referred to as the upper side, and the needle valve side is referred to as the lower side. The "orifice" is the clearance between the needle valve and the valve seat when the valve is open. It is the "orifice cross-sectional area". The term "orifice" refers to a flow path from the valve seat to the boundary with the rectifying hole, which is a portion on the downstream side. Furthermore, the term "channel cross-sectional area" refers to the cross-sectional area of the channel perpendicular to the direction in which the coolant flows.

(Configuration of flow control valve)
The motor-operated valve 1 includes a bottomed cylindrical valve body 10 whose upper end is open, a topped cylindrical can 45 whose lower end is hermetically joined to the upper end surface of the valve body 10 by welding or the like, and an inner side of the valve body 10. , a valve shaft 21 arranged inside the guide stem 15, and a rotor 30 connected and fixed to the valve shaft 21 so as to be integrally rotatable. A stator fitted around the outer periphery of the can 45 is arranged around the rotor 30 to rotate the rotor 30, but the illustration thereof is omitted here. The rotor 30 and stator constitute a stepping motor. Let L be the axis of the motor operated valve 1 .

The valve body 10 is formed by connecting a hollow cylindrical portion 10a and a bottom wall portion 10b. The valve body 10 can be formed by press-molding a plate material made of SUS, but may be formed by forging a SUS material. However, the valve body 10 can be formed by using a material other than SUS (stainless steel) (for example, brass), and by using a processing method other than pressing or forging (for example, cutting).

A circular opening 10d is formed in the center of the bottom wall portion 10b, and a valve seat member 11 is fixed to the opening 10d by brazing or the like.

2 is a longitudinal sectional view of the valve seat member 11, FIG. 3 is a perspective view of the valve seat member 11 viewed from below, and FIG. 4 is a bottom view of the valve seat member 11. As shown in FIG.

The substantially cylindrical valve seat member 11 includes an upper cylindrical portion 11a, a middle cylindrical portion 11b having a larger diameter than the upper cylindrical portion 11a, a lower cylindrical portion 11c having a larger diameter than the middle cylindrical portion 11b, a middle cylindrical portion 11b, and a lower portion. A partition wall portion 11d extending radially inward from the vicinity of the boundary of the cylindrical portion 11c and an inner cylindrical portion 11e extending downward from the partition wall portion 11d are continuously provided. The lower end of the inner cylindrical portion 11e is provided with a frusto-conical portion 11f.

The middle cylindrical portion 11b is fitted into the opening 10d, the upper cylindrical portion 11a protrudes into the valve body 10, and the lower cylindrical portion 11c is disposed outside the valve body 10. As shown in FIG. An annular space SP is formed between the lower cylindrical portion 11c and the inner cylindrical portion 11e. A stepped portion 11g is formed on the inner peripheral side of the lower end of the lower cylindrical portion 11c. The end of the first pipe T1 (FIG. 1) that has entered the annular space SP is fitted on the outer periphery of the inner cylindrical portion 11e and connected by brazing or the like. The stepped portion 11g serves as a portion for storing brazing material when brazing the pipe T1.

A cylindrical hole 11i extending downward along the axis L from the upper end of the inner cylindrical portion 11e to the bottom wall 11h is formed coaxially with the axis L. As shown in FIG. Four rectifying holes 11j extending obliquely outward from the outer circumference of the lower end of the cylindrical hole 11i are branched in the circumferential direction and are formed at equal intervals. Located on the outer circumference. Therefore, the straightening hole 11j faces the inner wall of the first pipe T1 assembled to the valve seat member 11. Specifically, when the cross section of the straightening hole 11j is projected along the central axis X of the straightening hole 11j, Then, the projected image overlaps with the inner wall of the first pipe T1. In other words, the central axis line X of the straightening hole 11j intersects the inner wall of the first pipe T1. The central axis X of the rectifying hole 11j forms an intersection angle θ of more than 0 degrees and less than 90 degrees with respect to the axis L (the angle formed by the central axis X and the axis L extending downward from the intersection with the central axis X). , hereinafter the same). Although the number of rectifying holes 11j may be two, three, or five or more, it is preferable that they are arranged at regular intervals in the circumferential direction. Cylindrical hole 11i constitutes an orifice. A valve seat 11k is formed on the inner circumference of the upper end of the inner cylindrical portion 11e. In addition, in a structure in which the central axis X and the axis L do not spatially intersect (there is a twist relationship), the central axis X and the axis L intersect when viewed from the side (viewpoint from the direction perpendicular to the axis L). Let the angle be the intersection angle θ.

In this embodiment, the length of the straightening hole 11j is longer than the inner diameter of the straightening hole 11j and longer than the inner radius of the cylindrical hole 11i. The length of the rectifying hole 11j is defined as a pair of line segments in which the inner wall of the rectifying hole 11j sandwiches the central axis X in a cross section (here, FIG. 2) obtained by cutting the motor-operated valve 1 along a plane passing through the axis L and the central axis X. A straight line (dotted line in FIG. 2) PL1 connecting one ends of the line segments of the inner wall and a straight line (dotted line in FIG. 2) PL2 connecting the other ends of the inner wall segments are connected to points PT1 and PT2. The distance between the points PT1 and PT2 when they intersect with .

Furthermore, the total cross-sectional area of the four rectifying holes 11j is the flow formed between the conical portion 25d and the valve seat 11k when the needle valve (valve element) 25 is at its maximum lift (maximum valve opening). larger than the passage cross-sectional area (ie, orifice cross-sectional area). Further, the channel cross-sectional area of the cylindrical hole 11i is equal to or larger than the orifice cross-sectional area at the time of maximum valve opening. It is preferable that the total flow cross-sectional area of the rectifying holes 11j is larger than the flow channel cross-sectional area of the cylindrical holes 11i.

In FIG. 1, an inlet opening 10e is formed in the hollow cylindrical portion 10a of the valve body 10, and the end of the second pipe T2 is inserted into the inlet opening 10e and connected by brazing or the like. Let O be the axis of the entrance opening 10e.

With the lower end of the can 45 abutting against the upper end of the valve body 10, the collar-shaped disk 18 is fitted to the inner circumference of the lower end of the can 45, and these are joined by welding. As a result, the valve body 10 and the can 45 are integrated in a hermetically sealed state.

The brim-shaped disk 18 has a plurality of through holes (not shown) through which the refrigerant can move between the valve body 10 side and the can 45 side.

The resin-made guide stem 15 disposed inside the rotor 30 comprises a solid cylindrical main body 15a and a hollow cylindrical portion 15b. The main body 15a has a female threaded hole 15c along the axis L. As shown in FIG. A movable stopper 35 for the valve closing direction is installed above the guide stem 15 .

A brim-shaped disk 18 welded to the upper end of the valve body 10 is disposed on the outer periphery of the intermediate portion of the hollow cylindrical portion 15b. Fixed. A pressure equalizing hole 15d is formed in the hollow cylindrical portion 15b.

In order to set the origin position for control of the rotor 30 and the valve shaft 21, a fixed stopper 55 for the valve closing direction having a rectangular cross section is provided on the upper surface of the main body 15a of the guide stem 15, and protrudes upward. A valve-opening direction fixed stopper 56 having a rectangular cross section projects downward from the lower surface of the main body 15 a of the guide stem 15 . Here, the origin position for control of the rotor 30 and the valve shaft 21 means that the movable stopper 35 for the valve-closing direction is in contact with the fixed stopper 55 for the valve-closing direction, and the rotor 30 and the valve shaft 21 are at the lowest position. is the position when it reaches

The valve shaft 21 made of metal has an end portion 21a to which an annular connecting body 32 attached to the rotor 30 is fitted, a male threaded portion 21b screwed into the female threaded hole 15c, and a flange portion 21c formed near the lower end. and a lower end connecting portion 21d are coaxially connected.

A movable stopper 35 for the valve closing direction fixed to the valve shaft 21 is arranged near the upper end of the male screw portion 21 b and is engaged with the lower surface of the upper wall of the rotor 30 . A stopper portion 35a having a rectangular cross section is formed on the lower surface of the movable stopper 35 for the valve closing direction.

A valve-opening direction movable stopper 36 is press-fitted near the lower end of the male threaded portion 21b of the valve shaft 21 so as to abut against the upper surface of the brim portion 21c. A stopper portion 36a having a rectangular cross section is formed on the upper surface of the movable stopper 36 for the valve opening direction. Here, the valve opening direction movable stopper 36 and the valve shaft 21 are fixed by forming a female thread on the inner periphery of the valve opening direction movable stopper 36 and screwing it with the male threaded portion 21b.

Below the valve shaft 21, a valve holder 23 is slidably fitted inside the hollow cylindrical portion 15b. The valve holder 23 has a truncated cylindrical shape in which a hollow cylindrical portion 23a and an upper wall 23b are connected. A stepped opening 23c is formed in the center of the upper wall 23b, and the hollow cylindrical portion 23a has a communicating hole 23d. The open lower end of the hollow cylindrical portion 23a of the valve holder 23 is arranged below the second pipe T2 in the valve closed state and closed by an annular member 27 which is crimped and fixed.

The lower end connecting portion 21d passes through the stepped opening 23c in a state where the flange portion 21c of the valve shaft 21 is in contact with the stepped portion of the stepped opening 23c. By processing, the valve shaft 21 and the valve holder 23 are fixedly connected. A valve chamber 29 is defined between the valve body 10 and the valve holder 23 .

A needle valve 25 is arranged to protrude from the valve holder 23 through the annular member 27 . The needle valve 25 includes a cylindrical shaft portion 25a, a valve collar portion 25b, a valve cylindrical portion 25c, a conical portion 25d whose diameter decreases downward, and a plurality of conical tapered portions formed in stages. 25e. The taper angle (the angle intersecting the axis L) of the conical portion 25d is greater than the taper angle of the tapered portion 25e that contacts the conical portion 25d.

A ring-shaped member 31 is fitted to the outer periphery of the shaft portion 25a by press fitting or the like. Since the outer diameter of the ring-shaped member 31 is larger than the inner diameter of the annular member 27 , the needle valve 25 is prevented from falling off from the valve holder 23 . A washer 28 is provided between the ring-shaped member 31 and the annular member 27 to reduce friction during relative rotation between the ring-shaped member 31 and the annular member 27 .

Between the upper wall 23b of the valve holder 23 and the needle valve 25, a cylindrical spring receiving member 26 having a lower flange 26a is arranged. A coil spring 24 is arranged between the upper wall 23b and the lower flange 26a to urge the spring receiving member 26 downward against the valve holder 23. As shown in FIG.

When the conical portion 25d is seated on the valve seat 11k of the valve seat member 11 and receives an upward reaction force, the spring bearing member 26 urged upward by the needle valve 25 is pushed upward by the upper wall 23b of the valve holder 23. The needle valve 25 is axially locked to the valve shaft 21 by contacting the lower surface (or the lower end connecting portion 21d).

The valve shaft 21, the valve holder 23, the needle valve 25, and the coil spring 24 are substantially integrated with the guide stem 15 when the needle valve 25 is separated from the valve seat 11k (valve open state). ascends and descends while rotating.

(Operation of flow control valve)
The operation of the motor operated valve 1 will be specifically described.
Here, it is assumed that refrigerant (fluid) is entering the valve chamber 29 from the second pipe T2.

Pulse power is supplied to a stator (not shown) from an external control device to rotate the rotor 30 and the valve shaft 21 in one direction. The valve closing direction movable stopper 35 descends while rotating, and the needle valve 25 is seated on the valve seat 11k to close the orifice. This blocks the flow of refrigerant from the valve chamber 29 toward the first pipe T1.

At this time, the movable stopper 35 is not yet in contact with the fixed stopper 55, the rotor 30 and the valve shaft 21 do not stop rotating, and pulse power supply continues until the coil spring 24 is compressed by a predetermined amount. As a result, the rotation of the needle valve 25 is restrained while being seated on the valve seat 11k, while the rotor 30, the valve shaft 21, the valve holder 23, and the like further rotate and descend.

At this time, since the valve shaft 21 and the valve holder 23 are lowered with respect to the seated needle valve 25 , the coil spring 24 is contracted and compressed, thereby absorbing the downward force of the valve shaft 21 and the valve holder 23 . After that, when the amount of compression of the coil spring 24 reaches a predetermined amount, the movable stopper 35 abuts against the fixed stopper 55 and is locked, the rotor 30 and the valve shaft 21 reach the lowest position, and pulse power supply to the stator continues. Even if this is done, the descent of the rotor 30 and the valve stem 21 is forcibly stopped.

In this manner, even after the needle valve 25 is seated on the valve seat 11k and the orifice 11d is closed, the rotor 10 is still maintained until the movable stopper 35 reaches the control origin position where the movable stopper 35 abuts against the fixed stopper 55 and is locked. 30, the valve stem 21, and the valve holder 23 continue to rotate downward, and the coil spring 24 is compressed. Therefore, the needle valve 25 is strongly pressed against the valve seat 11k by the urging force of the coil spring 24, thereby reliably preventing refrigerant leakage and the like.

On the other hand, when a reverse polarity pulse power supply is applied to the stator from the control origin position, the rotor 30 and the valve shaft 21 are driven to rotate in the direction opposite to the direction when the valve is closed, and the screw feed is formed by the female screw hole 15c and the male screw portion 21b. The mechanism raises the rotor 30, the valve shaft 21, the valve holder 23, and the valve-opening direction movable stopper 36 while rotating. As a result, the pressing force applied to the needle valve 25 is weakened, the coil spring 24 is expanded, and when the needle valve 25 is separated from the valve seat 11k, the orifice is opened. As a result, the refrigerant that has entered the valve chamber 29 from the second pipe T2 passes through the gap between the conical portion 25d and the valve seat 11k, passes through the cylindrical hole 11i, and enters the first pipe T1. flow.

In this case, since the lift amount of the needle valve 25 is determined according to the pulse power supply to the stator, the refrigerant flow rate can be controlled. By continuing the pulse power supply, the needle valve 25 is finally fully opened. When the pulse power supply continues, the movable stopper 36 abuts against the valve-opening direction fixed stopper 56 and is locked, thereby forcibly rotating and lifting the rotor 30, the valve shaft 21, and the valve holder 23. be stopped.

According to this embodiment, when the valve is opened, the refrigerant that has passed through the gap between the conical portion 25d and the valve seat 11k and entered the cylindrical hole 11i of the valve seat member 11 abuts the bottom wall 11h and is prevented from flowing. The direction is changed and it flows out of the valve seat member 11 through the cylindrical rectifying hole 11j. At this time, since the refrigerant exhibits a rectifying effect by passing through the rectifying hole 11j, the bubbles in the gas-liquid two-phase state and the bubbles generated when passing through the orifice are miniaturized, reducing noise when the bubbles burst. can. In addition, since the refrigerant passes through the four regulating holes 11j, the force of the flow is dispersed, pressure recovery is hastened, and the generation of air bubbles that cause noise can be suppressed. Further, by imparting a rectifying effect to the valve seat member 11, there is no need to provide a separate rectifying member, and the number of parts can be reduced.

In addition, according to the present embodiment, the refrigerant that has passed through the cylindrical hole 11i, which is the orifice portion, flows out from the rectifying hole 11j so as to collide with the inner wall of the first pipe T1. , and the refrigerant pressure can be restored before turbulence occurs. As a result, it is possible to suppress the generation of air bubbles that cause noise.

When the refrigerant flows from the first pipe T1 toward the second pipe T2, the refrigerant entering the valve seat member 11 from the first pipe T1 is redirected by the rectifying holes 11j and flows straight. Do not go to the orifice. Therefore, since the refrigerant having a high flow velocity does not pass through the orifice, vibration of the needle valve 25 when the valve is opened can be suppressed.

[Second embodiment]
FIG. 5 is a vertical cross-sectional view of a valve seat member 11A that can be used in the electric valve according to the second embodiment. The configuration of the motor-operated valve other than the valve seat member 11A is the same as that of the first embodiment, so redundant description will be omitted.

A valve seat member 11A of the present embodiment differs from the valve seat member 11 shown in FIG. 2 mainly in that a bottom wall 11Ah is formed with a tapered portion 11Am that serves as a lower end of a cylindrical hole 11Ai. A portion of the tapered portion 11Am is in contact with the rectifying hole 11Aj. The central axis X of the rectifying hole 11Aj intersects the inner wall of the first pipe T1 (see FIG. 1). The center axis X of the rectifying hole 11Aj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. Also in this embodiment, the lower end of the inner cylindrical portion 11Ae is provided with a truncated conical portion 11Af. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The refrigerant that has passed through the orifice when the valve is open flows along the cylindrical hole 11Ai, which is the orifice, and reaches the tapered portion 11Am. At least part of the refrigerant stays in the tapered portion 11Am and then enters the rectifying holes 11Aj, so that the refrigerant pressure can be easily recovered. Moreover, when the coolant passes through the edge of the tapered portion 11Am, there is also an effect of dispersing air bubbles. The tapered portion 11Am can be formed by transferring the tip shape of the tool when forming the cylindrical hole 11Ai using a cutting tool such as a drill.

[Third embodiment]
FIG. 6 is a vertical cross-sectional view of a valve seat member 11B that can be used in the electric valve according to the third embodiment. The configuration of the motor-operated valve other than the valve seat member 11B is the same as that of the first embodiment, so redundant description will be omitted.

The valve seat member 11B of this embodiment penetrates the bottom wall 11Bh in parallel with the axis L from the intermediate position of each rectifying hole 11Bj with respect to the valve seat member 11 shown in FIG. The main difference is that a communication opening 11Bm located on the top surface (lower surface) of 11f is formed. The inner diameter of the communication opening 11Bm is preferably 1/4 or less of the inner diameter of the rectifying hole Bj. The central axis X of the rectifying hole 11Bj intersects the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Bj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. Also in this embodiment, the lower end of the inner cylindrical portion 11Be is provided with a truncated conical portion 11Bf. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The refrigerant that has passed through the orifice when the valve is open flows along the cylindrical hole 11Bi, which is the orifice, and reaches the bottom wall 11Bh. From here, the refrigerant passes through the rectifying holes 11Bj and flows out of the valve seat member 11B, but at that time, the refrigerant may collide with the inner wall of the first pipe T1 to form a vortex. Such a vortex may impede pressure recovery of the refrigerant.

In contrast, according to the present embodiment, negative pressure is generated inside the communication opening 11Bm when the refrigerant passes through the upper end of the communication opening 11Bm, so the refrigerant is sucked up from the lower end of the communication opening 11Bm. As a result, the vortex formed by colliding with the inner wall of the first pipe T1 can be quickly extinguished.

[Fourth embodiment]
FIG. 7 is a vertical cross-sectional view of a valve seat member 11C that can be used in the electric valve according to the fourth embodiment. The configuration of the motor-operated valve other than the valve seat member 11C is the same as that of the first embodiment, so redundant description will be omitted.

The valve seat member 11C of this embodiment differs mainly in the shape of the inner cylindrical portion 11Ce and the rectifying hole 11Cj. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The inner cylindrical portion 11Ce extending downward from the partition wall portion 11d is composed of an enlarged diameter portion 11Ce1 on the partition wall portion 11d side and a reduced diameter portion 11Ce2 on the distal end side whose outer diameter is smaller than that of the enlarged diameter portion 11Ce1. The first pipe T1 (FIG. 1) is fitted only to the enlarged diameter portion 11Ce1.

From the lower end of a cylindrical hole 11Ci formed inside the inner cylindrical portion 11Ce, a plurality of rectifying holes 11Cj are formed so as to obliquely extend toward the valve seat 11k side. The straightening hole 11Cj faces the inner wall of the first pipe T1 assembled to the valve seat member 11C. That is, the central axis line X of the straightening hole 11Cj intersects the inner wall of the first pipe T1 (see FIG. 1). The central axis line X of the rectifying hole 11Cj intersects the axis line L at an intersection angle θ of more than 90 degrees and less than 180 degrees.

Also in this embodiment, the length of the straightening hole 11Cj (the shortest length of the hole inner wall in the axial direction) is longer than the inner diameter of the straightening hole 11Cj and longer than the inner radius of the cylindrical hole 11Ci. In addition, the sum of the channel cross-sectional areas of the four rectifying holes 11Cj is larger than the orifice cross-sectional area at the time of maximum valve opening. Further, the channel cross-sectional area of the cylindrical hole 11Ci is equal to or larger than the orifice cross-sectional area at the time of maximum valve opening. It is preferable that the total cross-sectional area of the rectifying holes 11Cj is larger than the cross-sectional area of the cylindrical holes 11Ci.

The refrigerant that has passed through the orifice when the valve is open flows along the cylindrical hole 11Ci, which is the orifice, and reaches the bottom wall 11Ch. Here, the direction of flow of the refrigerant is bent at an acute angle, passes through the rectifying holes 11Cj, and flows out of the valve seat member 11C.

Since there is a gap between the first pipe T1 and the diameter-reduced portion 11Ce2, the refrigerant flowing out from the diameter-reduced portion 11Ce2 hits the inner wall of the first pipe T1, and further flows between the first pipe T1 and the diameter-reduced portion 11Ce2. It passes through the gap and goes downward. At this time, the flow velocity of the refrigerant flowing out from between the first pipe T1 and the diameter-reduced portion 11Ce2 becomes lower than the flow velocity of the refrigerant passing through the orifice cross-sectional area at the time of maximum valve opening.

[Fifth embodiment]
FIG. 8 is a vertical cross-sectional view of a valve seat member 11D that can be used in the electric valve according to the fifth embodiment. The configuration of the motor-operated valve other than the valve seat member 11D is the same as that of the first embodiment, so redundant description will be omitted.

The valve seat member 11D of this embodiment differs mainly in the shape of the inner cylindrical portion 11De and the rectifying hole 11Dj. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The inner cylindrical portion 11De extending downward from the partition wall portion 11d is composed of an enlarged diameter portion 11De1 on the partition wall portion 11d side and a reduced diameter portion 11De2 on the distal end side whose outer diameter is smaller than that of the enlarged diameter portion 11De1. The first pipe T1 (FIG. 1) is fitted only to the enlarged diameter portion 11De1.

From the lower end of the cylindrical hole 11Di formed inside the inner cylindrical portion 11De, the rectifying hole 11Dj is formed to extend in the direction perpendicular to the axis L. The holes 11Dj intersect at right angles. The rectifying hole 11Dj faces the inner wall of the first pipe T1 attached to the valve seat member 11D. In other words, the central axis line X of the straightening hole 11Dj intersects the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Dj intersects the axis L at an intersection angle θ of 90 degrees.

Also in this embodiment, it is preferable that the length of the straightening hole 11Dj is longer than the inner diameter of the straightening hole 11Dj and longer than the inner peripheral radius of the cylindrical hole 11Di. Further, the flow channel cross-sectional area of the rectifying hole 11Dj is larger than the orifice cross-sectional area at the time of maximum valve opening. Moreover, the minimum channel cross-sectional area of the cylindrical hole 11Di is equal to or larger than the orifice cross-sectional area at the time of maximum valve opening. It is preferable that the channel cross-sectional area of the rectifying hole 11Dj is larger than the channel cross-sectional area of the cylindrical hole 11Di.

The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Di that is the orifice portion and reaches the bottom wall 11Dh. Here, the direction of flow of the refrigerant is bent at a right angle, and flows out of the valve seat member 11D through the rectifying holes 11Dj.

Since there is a gap between the first pipe T1 and the diameter-reduced portion 11De2, the refrigerant flowing out from the diameter-reduced portion 11De2 hits the inner wall of the first pipe T1, and further flows between the first pipe T1 and the diameter-reduced portion 11De2. It passes through the gap and goes downward. At this time, the flow velocity of the refrigerant flowing out from between the first pipe T1 and the reduced diameter portion 11De2 becomes lower than the flow velocity of the refrigerant passing through the orifice cross-sectional area at the time of maximum valve opening.

[Sixth embodiment]
FIG. 9 is a vertical cross-sectional view of a valve seat member 11E that can be used in the electric valve according to the sixth embodiment. The configuration of the electric valve other than the valve seat member 11E is the same as that of the first embodiment, so redundant description will be omitted.

The valve seat member 11E of this embodiment differs mainly in the shape of the cylindrical hole 11Ei. Also in the present embodiment, the central axis X of the straightening hole 11Ej intersects the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Ej intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ee is provided with a truncated conical portion 11Ef. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The cylindrical hole 11Ei has a first hole 11Ei1 arranged below the valve seat 11k, a second hole 11Ei2 larger in diameter than the first hole 11Ei1, and a third hole 11Ei3 larger in diameter than the second hole 11Ei2. . The first hole 11Ei1 and the second hole 11Ei2 are connected by a first tapered portion 11Ei4, and the second hole 11Ei2 and the third hole 11Ei3 are connected by a second tapered portion 11Ei5. Four rectifying holes 11Ej communicate with the lower end of the third hole 11Ei3 (and the second tapered portion 11Ei5). The cylindrical hole 11Ei can be formed by processing, for example, using an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. Also, the cross-sectional area of the flow path of the first hole 11Ei1 is equal to or larger than the cross-sectional area of the orifice at the time of maximum valve opening. It is preferable that the total flow channel cross-sectional area of the rectifying holes 11Ej is larger than the flow channel cross-sectional area of the first holes 11Ei1.

The refrigerant that has passed through the orifice when the valve is open flows along the first hole 11Ei1, the first tapered portion 11Ei4, the second hole 11Ei2, the second tapered portion 11Ei5, and the third hole 11Ei3, and reaches the bottom wall 11Eh. . At this time, the channel cross-sectional area expands in three steps from the orifice to the bottom wall 11Eh. As a result, the refrigerant pressure can be gradually restored.

Furthermore, the refrigerant flows out of the valve seat member 11E through the rectifying holes 11Ej facing obliquely downward, and hits the inner wall of the first pipe T1, thereby forcibly reducing the flow velocity of the refrigerant, Refrigerant pressure can be restored before turbulence occurs.

[Seventh embodiment]
FIG. 10 is a vertical cross-sectional view of a valve seat member 11F that can be used in the electrically operated valve according to the seventh embodiment. The configuration of the motor-operated valve other than the valve seat member 11F is the same as that of the first embodiment, so redundant description will be omitted.

The valve seat member 11F of this embodiment differs mainly in the shape of the cylindrical hole 11Fi. Also in the present embodiment, the central axis X of the straightening hole 11Fj intersects the inner wall of the first pipe T1 (see FIG. 1). The center axis X of the rectifying hole 11Fj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Fe is provided with a truncated conical portion 11Ff. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The cylindrical hole 11Fi has a first hole 11Fi1 arranged below the valve seat 11k and a second hole 11Fi2 having a larger diameter than the first hole 11Fi1. The first hole 11Fi1 and the second hole 11Fi2 are connected by a tapered portion 11Fi3. Four straightening holes 11Fj communicate with the lower ends of the second holes 11Fi2. The cylindrical hole 11Fi can be formed by processing, for example, using an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. Also, the cross-sectional area of the flow path of the first hole 11Fi1 is equal to or larger than the cross-sectional area of the orifice at the time of maximum valve opening. It is preferable that the total flow channel cross-sectional area of the rectifying holes 11Fj is larger than the flow channel cross-sectional area of the first holes 11Fi1.

Refrigerant that has passed through the orifice when the valve is open flows along the first hole 11Fi1, the tapered portion 11Fi3, and the second hole 11Fi2 to reach the bottom wall 11Fh. At this time, the channel cross-sectional area expands in two steps from the orifice to the bottom wall 11Fh. As a result, the refrigerant pressure can be gradually restored.

Furthermore, the refrigerant flows out of the valve seat member 11F through the straightening holes 11Fj facing obliquely downward, and hits the inner wall of the first pipe T1, thereby forcibly reducing the flow velocity of the refrigerant, Refrigerant pressure can be restored before turbulence occurs.

[Eighth embodiment]
FIG. 11 is a vertical cross-sectional view of a valve seat member 11G that can be used in the electric valve according to the eighth embodiment. The configuration of the motor operated valve other than the valve seat member 11G is the same as that of the first embodiment, so redundant description will be omitted.

The valve seat member 11G of this embodiment is mainly different in that a central hole 11Gn connected to the cylindrical hole 11Gi is formed in the bottom wall 11Gh. Also in the present embodiment, the central axis X of the straightening hole 11Gj intersects the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Gj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ge is provided with a truncated conical portion 11Gf. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The central hole 11Gn is coaxial with the cylindrical hole 11Gi and has an inner diameter smaller than the inner diameters of the cylindrical hole 11Gi and the rectifying hole 11Gj. End portions of the cylindrical hole 11Gi and the rectifying hole 11Gj may be in contact with each other, or may be separated from each other.

The refrigerant that has passed through the orifice when the valve is open flows along the cylindrical hole 11Gi, which is the orifice, and reaches the bottom wall 11Gh. Here, part of the refrigerant passes through the rectifying holes 11Gj and flows out of the valve seat member 11G, and collides with the first pipe T1, which may form a vortex. On the other hand, the rest of the refrigerant that has reached the bottom wall 11Gh passes straight through the central hole 11Gn and flows out of the valve seat member 11G. It has the effect of disappearing. As a result, the pressure of the refrigerant can be quickly recovered.

[Ninth Embodiment]
FIG. 12 is a vertical cross-sectional view of a valve seat member 11H that can be used in an electrically operated valve according to the ninth embodiment. The configuration of the electric valve other than the valve seat member 11H is the same as that of the first embodiment, so redundant description will be omitted.

Referring to FIG. 12, the length of the rectifying hole 11Hj is such that the inner wall of the rectifying hole 11Hj crosses the central axis X in a cross section (here, FIG. 12) obtained by cutting the motor-operated valve 1 along a plane passing through the axis L and the central axis X. A straight line (dotted line in FIG. 12) PL1 connecting one ends of the line segments of the inner wall and a straight line (dotted line in FIG. 12) PL2 connecting the other ends of the line segments are represented by a pair of line segments sandwiched therebetween. It is the distance between the points PT1 and PT2 when the axis X intersects the points PT1 and PT2. Also in the present embodiment, the center axis X of the straightening hole 11Hj intersects the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Hj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11He is provided with a truncated conical portion 11Hf.

The valve seat member 11H of this embodiment is mainly different in the shape of the cylindrical hole 11Hi and in that the bottom wall 11Hh is formed with a central hole 11Hn connected to the cylindrical hole 11Hi. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The cylindrical hole 11Hi has a first hole 11Hi1 arranged below the valve seat 11k and a second hole 11Hi2 having a larger diameter than the first hole 11Hi1. The first hole 11Hi1 and the second hole 11Hi2 are connected by a tapered portion 11Hi3. Four rectifying holes 11Hj communicate with the lower ends of the second holes 11Hi2. The cylindrical hole 11Hi can be formed by processing, for example, using an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. Also, the cross-sectional area of the flow path of the first hole 11Hi1 is equal to or larger than the cross-sectional area of the orifice at the time of maximum valve opening. It is preferable that the total flow channel cross-sectional area of the rectifying holes 11Hj is larger than the flow channel cross-sectional area of the first holes 11Hi1.

The central hole 11Hn is coaxial with the cylindrical hole 11Hi and has an inner diameter smaller than the inner diameters of the cylindrical hole 11Hi and the rectifying hole 11Hj.

Refrigerant that has passed through the orifice when the valve is open flows along the first hole 11Hi1, the tapered portion 11Hi3, and the second hole 11Hi2 to reach the bottom wall 11Hh. At this time, the channel cross-sectional area expands in two steps from the orifice to the bottom wall 11Hh. As a result, the refrigerant pressure can be gradually restored.

Part of the refrigerant that has reached the bottom wall 11Hh passes through the rectifying holes 11Hj and flows out of the valve seat member 11H, and collides with the first pipe T1, which may form a vortex. . On the other hand, the rest of the refrigerant that has reached the bottom wall 11Hh passes straight through the central hole 11Hn and flows out of the valve seat member 11H. It has the effect of disappearing. Therefore, it is possible to quickly recover the pressure of the refrigerant.

[Tenth embodiment]
FIG. 13 is a vertical cross-sectional view of a valve seat member 11I that can be used in the electric valve according to the tenth embodiment. The configuration of the motor-operated valve other than the valve seat member 11I is the same as that of the first embodiment, so redundant description will be omitted.

The valve seat member 11I of this embodiment differs mainly in the positional relationship between the cylindrical hole 11Ii and the rectifying hole 11Ij. Also in the present embodiment, the central axis X of the straightening hole 11Ij intersects the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Ij intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. A lower end of the inner cylindrical portion 11Ie is provided with a truncated conical portion 11If. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

In this embodiment, the straightening hole 11Ij is connected between the lower end and the upper end of the cylindrical hole 11Ii. As a result, a coolant retention portion 11Ip is formed on the bottom wall 11Ih at the lower end of the cylindrical hole 11Ii up to the connecting portion with the rectifying hole 11Ij.

The refrigerant that has passed through the orifice when the valve is open flows along the cylindrical hole 11Ii, which is the orifice, and reaches the retention portion 11Ip of the bottom wall 11Ih. Here, the flow of the refrigerant makes a U-turn, passes through the regulating hole 11Ij, and flows out of the valve seat member 11I.

[Eleventh embodiment]
FIG. 14 is a vertical cross-sectional view of a valve seat member 11K that can be used in the electric valve according to the eleventh embodiment. The configuration of the motor-operated valve other than the valve seat member 11K is the same as that of the first embodiment, so redundant description will be omitted.

The valve seat member 11K of this embodiment differs mainly in the configuration of the inner cylindrical portion 11Ke. Also in the present embodiment, the central axis X of the straightening hole 11Kj intersects the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Kj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ke is provided with a truncated conical portion 11Kf. Configurations common to those of the first embodiment are denoted by the same reference numerals, and overlapping descriptions are omitted.

The inner cylindrical portion 11Ke extending downward from the partition wall portion 11d is composed of an enlarged diameter portion 11Ke1 on the partition wall portion 11d side and a reduced diameter portion 11Ke2 on the distal end side whose outer diameter is smaller than that of the enlarged diameter portion 11Ke1. A truncated conical portion 11Kf is formed at the lower end of the reduced diameter portion 11Ke2. The first pipe T1 (FIG. 1) is fitted only to the enlarged diameter portion 11Ke1.

From the lower end of a cylindrical hole 11Ki formed inside the inner cylindrical portion 11Ke, a plurality of rectifying holes 11Kj are formed so as to obliquely extend downward toward the valve seat 11k. Further, a communication opening 11Kn extending obliquely toward the partition wall portion 11d is formed from an intermediate position of each rectifying hole 11Kj. The inner diameter of the communication opening 11Kn is preferably 1/4 or less of the inner diameter of the rectifying hole Kj.

The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Ki, which is the orifice, and reaches the bottom wall 11Kh. From here, the refrigerant passes through the rectifying holes 11Kj and flows out to the outside of the valve seat member 11K. Such a vortex may impede pressure recovery of the refrigerant.

In contrast, according to the present embodiment, negative pressure is generated inside the communication opening 11Kn when the refrigerant passes through the lower end of the communication opening 11Kn, so the refrigerant is sucked through the upper end of the communication opening 11Kn. As a result, the vortex formed by colliding with the inner wall of the first pipe T1 can be quickly extinguished.

[Modification]
FIG. 15 is a diagram showing a configuration in which a valve seat member 11 and a porous filter FT that can be used in an electrically operated valve according to a modification of the present embodiment are combined. The right half is a side view. Since the configuration other than the porous filter FT is the same as that of the first embodiment, redundant description will be omitted.

A porous filter FT made of metal or resin is arranged around the inner cylindrical portion 11e of the valve seat member 11 so as to cover from the position indicated by the dotted line to below the truncated conical portion 11f. The porous filter FT is formed in a cylindrical shape from, for example, foam metal, mesh material, or punching metal, and is wound around the outer circumference of the inner cylindrical portion 11e so as to cover the outer ends of the rectifying holes 11j.

The refrigerant that has flowed out from the rectifying holes 11j passes through the porous filter FT, so that the air bubbles are subdivided, which is effective in further reducing noise. The valve seat member combined with the porous filter FT is not limited to the first embodiment, and may be combined with other embodiments.

In the above embodiment, when the intersection angle θ is less than 90 degrees, it is preferably 15 degrees or more and 75 degrees or less, more preferably 30 degrees or more and 60 degrees or less, and more than 90 degrees. In this case, the angle is preferably 105 degrees or more and 165 degrees or less, more preferably 120 degrees or more and 150 degrees or less.

1 Electric valve 10 Valve body 11 to 11K Valve seat member 11e Valve seat 15 Guide stem 21 Valve shaft 23 Valve holder 24 Coil spring 25 Needle valve 26 Spring receiving member 27 Annular member 29 Valve chamber 30 Rotor 35 Movable stopper 36 for valve closing direction Open Valve direction movable stopper 55 Valve closing direction fixed stopper 56 Valve opening direction fixed stopper FT Porous filter

Claims (15)

a valve body having a valve chamber;
a valve seat member attached to the valve body and having a valve seat;
a valve body arranged in the valve chamber and capable of moving up and down in a direction toward or away from the valve seat;
The valve seat member is connectable to a pipe and includes an orifice portion adjacent to the valve seat and a rectifying hole connected to the orifice portion,
A central axis of the straightening hole intersects the inner wall of the pipe,
A motor-operated valve characterized by: The rectifying hole branches into a plurality of lines from the orifice section,
The motor-operated valve according to claim 1, characterized in that: The total flow channel cross-sectional area of the rectifying hole is larger than the orifice cross-sectional area at the time of maximum valve opening,
The motor operated valve according to claim 1 or 2, characterized in that: The flow passage cross-sectional area of the orifice portion is equal to or greater than the orifice cross-sectional area at the time of maximum valve opening,
The motor-operated valve according to claim 3, characterized in that: The total flow channel cross-sectional area of the rectifying holes is larger than the flow channel cross-sectional area of the orifice,
5. The motor-operated valve according to claim 3 or 4, characterized in that: The length of the rectifying hole is longer than the inner diameter of the rectifying hole and longer than the inner circumference radius of the orifice section.
The motor-operated valve according to any one of claims 1 to 5, characterized in that: The valve seat member includes a cylindrical portion inside which the orifice portion is formed and which is disposed within the pipe.
The motor-operated valve according to any one of claims 1 to 6, characterized in that: A truncated conical portion is formed at the end of the cylindrical portion, and the outer end of the rectifying hole is located on the outer peripheral surface of the truncated conical portion.
The motor operated valve according to claim 7, characterized in that: A tapered portion is formed at an inner end of the orifice,
The motor-operated valve according to claim 7 or 8, characterized in that: a communicating opening extending from the rectifying hole to the outside of the valve seat member, the inner diameter of the communicating opening being smaller than the inner diameter of the rectifying hole;
The motor-operated valve according to any one of claims 7 to 9, characterized in that: the rectifying hole intersects the orifice,
The motor operated valve according to claim 7, characterized in that: The rectifying hole crosses the orifice at right angles,
The motor operated valve according to claim 7, characterized in that: The orifice portion has, in order from the valve seat side, a first hole and a second hole having a diameter larger than that of the first hole.
The motor-operated valve according to any one of claims 1 to 12, characterized in that: The orifice portion has, in order from the valve seat side, a first hole, a second hole having a larger diameter than the first hole, and a third hole having a larger diameter than the second hole.
The motor-operated valve according to any one of claims 1 to 12, characterized in that: a central hole connected to the orifice portion and extending in the same direction as the orifice portion, wherein the inner diameter of the central hole is smaller than the inner diameter of the rectifying hole;
The motor-operated valve according to any one of claims 1 to 14, characterized in that:

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