Motor-operated valve

Abstract

To provide an electric valve capable of further reducing noise while suppressing costs.SOLUTION: An electric valve has a valve body equipped with a valve chamber, a valve seat member provided on the valve body and equipped with a valve seat, and a valve element disposed in the valve chamber and capable of elevating / lowering in a direction approaching or separating from the valve seat. The valve seat member is equipped with an orifice portion that can be connected to piping and is adjacent to the valve seat, and a straightening hole that connects to the orifice portion. A center axis of the straightening hole is not parallel with an axis of the orifice portion and passes through a space between an inner peripheral surface of the orifice portion and the axis of the orifice portion without intersecting the axis of the orifice portion. When the axis of the orifice portion is projected in a normal direction on a surface including the center axis of the straightening hole and parallel with the axis of the orifice portion, the center axis of the straightening hole intersects the projected axis of the orifice portion, and across an intersecting point, the projected axis toward the valve seat side and the center axis toward a tip end side of the straightening hole form an obtuse angle.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a motor-operated valve. [Background technology]

[0002] An electric valve used as a flow control valve in a refrigeration cycle has a screw mechanism in which the male threaded portion of a valve shaft, which is rotated by a motor, is screwed into a female threaded hole provided in the valve body. This screw mechanism converts rotational motion into axial motion, thereby displacing the valve shaft in the axial direction and controlling the flow rate.

[0003] For example, Patent Document 1 discloses an electric valve in which a thin plate member (punched plate) with many small holes that perform a throttling function and a bubble-fragmenting function is attached to the main body and allows a refrigerant to pass through. Such a thin plate member performs a rectifying function for the refrigerant passing through in a two-phase flow state, a throttling function, and a function for fragmenting bubbles in the refrigerant in a two-phase flow state, and can effectively reduce the refrigerant passing noise caused by bubbles. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2007-107623 A Summary of the Invention [Problem to be solved by the invention]

[0005] In the refrigeration cycle, the refrigerant generally flows from the pipe into the valve body of the motor-operated valve in a gas-liquid two-phase flow state, so it inherently contains air bubbles. When the refrigerant passes through the orifice, a pressure drop occurs, generating air bubbles. When these bubbles burst, they generate noise.

[0006] According to the motor-operated valve of Patent Document 1, the refrigerant passing noise caused by air bubbles can be reduced, but there is room for further quieting.

[0007] The inventors discovered that in the motor-operated valve of Patent Document 1, when the refrigerant that has passed through the orifice passes through the small hole in the thin plate member during the pressure recovery process and enters the larger diameter pipe, turbulence occurs and noise is generated. In addition, the motor-operated valve of Patent Document 1 requires a thin plate member, which increases the number of parts and makes assembly more difficult.

[0008] SUMMARY OF THE PRESENT EMBODIMENT An object of the present invention is to provide an electrically operated valve that can further reduce noise while ensuring ease of assembly. [Means for solving the problem]

[0009] In order to solve the above problems, the motor-operated valve of the present invention comprises: A valve body having a valve chamber; a valve seat member provided on the valve body and having a valve seat; a valve body that is disposed in the valve chamber and is movable up and down in a direction toward or away from the valve seat, the valve seat member includes an orifice portion adjacent to the valve seat and a flow straightening hole communicating with the orifice portion, The valve seat member has a truncated cone portion, and an outlet of the flow straightening hole is formed on an outer circumferential surface of the truncated cone portion, a central axis of the flow straightening hole is not parallel to and does not intersect with the axis of the orifice portion, and passes between an inner circumferential surface of the orifice portion and the axis of the orifice portion, When the axis of the orifice portion is projected along the normal direction of a plane that includes the central axis of the flow straightening hole and is parallel to the axis of the orifice portion, the central axis of the flow straightening hole intersects with the projected axis of the orifice portion, and the projected axis toward the valve seat side and the central axis toward the tip side of the flow straightening hole form an obtuse angle on either side of the intersection. Effect of the Invention

[0010] According to the present invention, it is possible to provide a motor-operated valve that can further reduce noise while ensuring ease of assembly. [Brief description of the drawings]

[0011] [Figure 1] FIG. 1 is a vertical sectional view showing a motor-operated valve according to a first embodiment of the present invention. [Diagram 2] FIG. 2 is a vertical sectional view of the valve seat member according to the first embodiment. [Diagram 3] FIG. 3 is a perspective view of the valve seat member according to the first embodiment, as viewed from below. [Figure 4] FIG. 4 is a bottom view of the valve seat member according to the first embodiment. [Diagram 5] FIG. 5 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the second embodiment. [Figure 6] FIG. 6 is a bottom view of the valve seat member according to the second embodiment. [Figure 7] FIG. 7 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the third embodiment. [Figure 8] FIG. 8 is a bottom view of the valve seat member according to the third embodiment. [Figure 9] FIG. 9 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the fourth embodiment. [Figure 10] FIG. 10 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the fifth embodiment. [Figure 11] FIG. 11 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the sixth embodiment. [Figure 12] FIG. 12 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the seventh embodiment. [Figure 13] FIG. 13 is a bottom view of the valve seat member according to the seventh embodiment. [Figure 14] FIG. 14 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the eighth embodiment. [Figure 15] FIG. 15 is a bottom view of the valve seat member according to the eighth embodiment. [Figure 16] FIG. 16 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the ninth embodiment. [Figure 17]FIG. 17 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the tenth embodiment. [Figure 18] FIG. 18 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the eleventh embodiment. [Figure 19] FIG. 19 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the twelfth embodiment. [Figure 20] FIG. 20 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the thirteenth embodiment. [Figure 21] FIG. 21 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the fourteenth embodiment. [Figure 22] FIG. 22 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the fifteenth embodiment. [Diagram 23] FIG. 23 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the sixteenth embodiment. [Figure 24] FIG. 24 is a vertical sectional view of a valve seat member that can be used in the motor-operated valve according to the seventeenth embodiment. [Diagram 25] FIG. 25 is a diagram showing a configuration in which a valve seat member and a porous filter that can be used in a motor-operated valve according to a modified example of this embodiment are combined. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[0013] [First embodiment] FIG. 1 is a vertical cross-sectional view showing an electric valve 1 according to a first embodiment of the present 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 term "orifice" refers to the gap between the needle valve and the valve seat when the valve is open, and the area of ​​the annular surface formed by the outer diameter of the needle valve and the inner diameter of the valve seat at the position where the gap is smallest is the "orifice cross-sectional area." The term "orifice portion" refers to the flow path from the valve seat to the boundary with the flow straightening hole, which is a downstream portion. Furthermore, the term "flow path cross-sectional area" refers to the cross-sectional area of ​​the flow path perpendicular to the direction in which the refrigerant flows.

[0014] (Flow control valve configuration) The motor-operated valve 1 comprises a cylindrical valve body 10 with a bottom and an open top, a cylindrical can 45 with a top whose bottom end is hermetically joined by welding or the like to the top surface of the valve body 10, a guide stem 15 fixed to the inside of the valve body 10, a valve shaft 21 disposed 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 is disposed around the rotor 30 and fitted onto the outer periphery of the can 45 to rotate the rotor 30, but is not shown here. The rotor 30 and the stator form a stepping motor. The axis of the motor-operated valve 1 and the orifice is designated as L.

[0015] 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 SUS plate material, but it may also be formed by forging a SUS material. However, the valve body 10 can be formed of a material other than SUS (stainless steel) (e.g., brass) and can also be formed by a processing method other than pressing or forging (e.g., cutting).

[0016] 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.

[0017] Fig. 2 is a vertical cross-sectional view of the valve seat member 11, Fig. 3 is a perspective view of the valve seat member 11 seen from below, and Fig. 4 is a bottom view of the valve seat member 11. Note that the cross-sectional views may differ from the cross-sectional configuration that is actually observed.

[0018] The generally cylindrical valve seat member 11 is made up of 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 partition wall portion 11d extending radially inward from the boundary between the middle cylindrical portion 11b and the lower cylindrical portion 11c, and an inner cylindrical portion 11e extending downward from the partition wall portion 11d. The lower end of the inner cylindrical portion 11e is provided with a truncated cone portion 11f.

[0019] The middle cylindrical portion 11b fits into the opening 10d of the valve body 10, the upper cylindrical portion 11a protrudes into the inside of the valve body 10, and the lower cylindrical portion 11c is disposed outside the valve body 10. An annular space SP is formed between the lower cylindrical portion 11c and the inner cylindrical portion 11e. A step portion 11g is formed on the inner peripheral side of the lower end of the lower cylindrical portion 11c. The end portion of the first pipe T1 (FIG. 1) that has entered the annular space SP is inserted into the outer periphery of the inner cylindrical portion 11e and connected by brazing or the like. The step portion 11g becomes a portion for storing brazing material when the pipe T1 is brazed. In this specification, the first pipe T1 may be simply referred to as a pipe.

[0020] A cylindrical hole 11i is formed coaxially with the axis L, extending downward from the upper end of the inner cylindrical portion 11e along the axis L to the bottom wall 11h. A plurality of straightening holes 11j1, 11j2, 11j3, 11j4 (see FIG. 4) are formed at equal intervals and branch out in the circumferential direction, extending obliquely outward from the outer periphery of the lower end of the cylindrical hole 11i, and the outer end of each straightening hole is located on the outer periphery of the truncated cone portion 11f. The number of straightening holes may be two, three, or five or more. The same applies to embodiments described later other than the embodiment having a single straightening hole.

[0021] The cylindrical flow straightening holes 11j1, 11j2, 11j3, and 11j4 are inclined downward, and here, face the inner wall of the first pipe T1 assembled to the valve seat member 11. When the axis L is projected along the normal direction onto a plane that is parallel to the axis L and includes the central axes X1, X2, X3, and X4 of the flow straightening holes 11j1, 11j2, 11j3, and 11j4, the projected axis L intersects with the central axes X1, X2, X3, and X4 at an angle other than a right angle. The projected axis L toward the orifice side and the central axes X1, X2, X3, and X4 toward the tip side of the flow straightening holes form an obtuse angle on either side of the intersection.

[0022] Furthermore, the central axes X1, X2, X3, and X4 (FIG. 4) of the straightening holes 11j1, 11j2, 11j3, and 11j4 intersect the cylindrical hole 11i, but are in a twisted relationship with respect to the axis L, that is, do not spatially intersect with the axis L. In other words, the central axes X1, X2, X3, and X4 pass between the inner circumferential surface of the cylindrical hole 11i and the axis L. Here, the minimum distances Δ between the central axes X1, X2, X3, and X4 and the axis L are equal to each other, but may be different. When the inner diameter of the straightening hole is φ, the minimum distance Δ is preferably in the range of 0.3φ to 0.7φ. In other words, the minimum distance Δ between the central axes X1, X2, X3, and X4 of the straightening holes and the axis L of the orifice portion is preferably 0.3 to 0.7 times the inner diameter of the straightening hole. If the minimum distance Δ is too small, the effect of generating a swirling flow is small, whereas if the minimum distance Δ is too large, the motor-operated valve becomes large.

[0023] The number of the flow straightening holes may be two, three, or five or more, but it is preferable that they are arranged at equal intervals in the circumferential direction. The cylindrical hole 11i constitutes the orifice portion. A valve seat 11k is formed on the inner circumference of the upper end of the cylindrical hole 11i. The lengths and inner diameters of the flow straightening holes 11j1, 11j2, 11j3, and 11j4 are equal to each other, and these flow straightening holes have the same relationship in rotational symmetry with respect to the axis L. Therefore, the configuration of the flow straightening hole 11j1 will be described as a representative of the four flow straightening holes.

[0024] In this embodiment, the length of the flow straightening hole 11j1 is longer than the inner diameter of the flow straightening hole 11j1 and longer than the inner circumferential radius of the cylindrical hole 11i. The length of the flow straightening hole 11j1 refers to the distance between two points PT1 and PT2 when the inner wall of the flow straightening hole 11j1 is represented as a pair of line segments sandwiching the central axis X1 in a cross section of the motor-operated valve 1 cut by a plane that is parallel to the axis L and passes through the central axis X1, and the central axis X of the flow straightening hole 11j intersects with a straight line connecting one end of the line segments of the inner wall and a straight line connecting the other end of the line segments at points PT1 and PT2.

[0025] Furthermore, the total of the flow passage cross-sectional areas of the four flow straightening holes 11j1, 11j2, 11j3, and 11j4 is larger than the flow passage cross-sectional area (i.e., the orifice cross-sectional area) formed between the conical portion 25d and the valve seat 11k at the maximum lift (maximum opening) of the needle valve (valve body) 25. Also, the flow passage cross-sectional area of ​​the cylindrical hole 11i is equal to or larger than the orifice cross-sectional area at the maximum opening. It is preferable that the total of the flow passage cross-sectional areas of the flow straightening holes 11j1, 11j2, 11j3, and 11j4 is larger than the flow passage cross-sectional area of ​​the cylindrical hole 11i.

[0026] 1, an inlet opening 10e is formed in a hollow cylindrical portion 10a of a valve body 10, and an end portion of a second pipe T2 is inserted into the inlet opening 10e and connected by brazing or the like. The axis of the inlet opening 10e is designated as O.

[0027] With the lower end of the can 45 butted against the upper end of the valve body 10, the flange-shaped disk 18 is fitted onto the inner periphery 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 sealed state.

[0028] The flange-shaped disk 18 has a plurality of through holes (not shown), and the refrigerant can move between the valve body 10 side and the can 45 side via these through holes.

[0029] The resin guide stem 15 disposed inside the rotor 30 comprises a solid cylindrical body 15a and a hollow cylindrical portion 15b connected together. The body 15a has a female threaded hole 15c along the axis L. A valve closing direction movable stopper 35 is disposed above the guide stem 15.

[0030] A flange-shaped disk 18 welded to the upper end of the valve body 10 is disposed on the outer periphery of the middle part of the hollow cylindrical portion 15b, and the guide stem 15 is fixed to the valve body 10 via this flange-shaped disk 18. A pressure equalizing hole 15d is formed in the hollow cylindrical portion 15b.

[0031] In order to set the control origin position of the rotor 30 and the valve shaft 21, a valve closing direction fixed stopper 55 having a rectangular cross section is provided to protrude upward from the upper surface of the body 15a of the guide stem 15, and a valve opening direction fixed stopper 56 having a rectangular cross section is provided to protrude downward from the lower surface of the body 15a of the guide stem 15. Here, the control origin position of the rotor 30 and the valve shaft 21 refers to the position when the valve closing direction movable stopper 35 abuts against and is locked against the valve closing direction fixed stopper 55, and the rotor 30 and the valve shaft 21 reach their lowest positions.

[0032] The metallic valve shaft 21 comprises an end portion 21a fitted with an annular connecting body 32 attached to the rotor 30, a male threaded portion 21b which screws into the female threaded hole 15c, a flange-shaped portion 21c formed near the lower end, and a lower end connecting portion 21d, all of which are coaxially connected.

[0033] A valve closing direction movable stopper 35 fixed to the valve shaft 21 is disposed near the upper end of the male thread portion 21b and 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 valve closing direction movable stopper 35.

[0034] Further, 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 flange-shaped portion 21c. A stopper portion 36a having a rectangular cross section is formed on the upper surface of the valve-opening direction movable stopper 36. Here, a female thread is formed on the inner periphery of the valve-opening direction movable stopper 36, and the valve-opening direction movable stopper 36 is fixed to the valve shaft 21 by screwing it into the male threaded portion 21b.

[0035] The valve holder 23 is disposed below the valve shaft 21 and slidably fitted inside the hollow cylindrical portion 15b. The valve holder 23 has a topped cylindrical shape with a hollow cylindrical portion 23a and an upper wall 23b connected to each other. A stepped opening 23c is formed in the center of the upper wall 23b, and the hollow cylindrical portion 23a has a communication hole 23d. The open lower end of the hollow cylindrical portion 23a of the valve holder 23 is disposed below the second pipe T2 in the valve closed state and is closed by an annular member 27 fixed by crimping.

[0036] With the flange portion 21c of the valve shaft 21 abutting against the step of the stepped opening 23c, the lower end connecting portion 21d passes through the stepped opening 23c, and the lower end connecting portion 21d is crimped to expand its diameter, thereby fixedly connecting the valve shaft 21 to the valve holder 23. A valve chamber 29 is defined between the valve body 10 and the valve holder 23.

[0037] The needle valve 25 is disposed so as to protrude from the valve holder 23 through the annular member 27. The needle valve 25 is composed of a cylindrical shaft portion 25a, a valve flange portion 25b, a valve cylinder portion 25c, a conical portion 25d that decreases in diameter downward, and a tapered portion 25e having a plurality of stepwise conical shapes, which are connected together. The taper angle of the conical portion 25d (the angle at which it intersects with the axis L) is larger than the taper angle of the tapered portion 25e that is in contact with the conical portion 25d.

[0038] A ring-shaped member 31 is fitted onto the outer periphery of the shaft portion 25a by press fitting or the like. The outer diameter of the ring-shaped member 31 is larger than the inner diameter of the annular member 27, so that the needle valve 25 is prevented from falling off the valve holder 23. A washer 28 is disposed 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.

[0039] A cylindrical spring receiving member 26 having a lower end flange 26a is disposed between the upper wall 23b of the valve holder 23 and the needle valve 25. Furthermore, a coil spring 24 is disposed between the upper wall 23b and the lower end flange 26a, and biases the spring receiving member 26 downward relative to the valve holder 23.

[0040] When the conical portion 25d seats on the valve seat 11k of the valve seat member 11 and receives an upward reaction force, the spring support member 26, which is biased upward by the needle valve 25, abuts against the lower surface (or the lower end connecting portion 21d) of the upper wall 23b of the valve holder 23, and the needle valve 25 is axially engaged with the valve shaft 21.

[0041] The valve shaft 21, valve holder 23, needle valve 25, and coil spring 24 move up and down while rotating substantially integrally with the guide stem 15 when the needle valve 25 is separated from the valve seat 11k (valve open state).

[0042] (Flow control valve operation) The operation of the motor-operated valve 1 will now be described in detail. Here, it is assumed that the refrigerant (fluid) enters the valve chamber 29 from the second pipe T2.

[0043] When a pulse current is supplied from an external control device to a stator (not shown), the rotor 30 and the valve shaft 21 are rotated in one direction, and the valve shaft 21 and the valve closing direction movable stopper 35 are lowered while rotating by a screw feed mechanism consisting of the female screw hole 15c and the male screw portion 21b, 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 chest 29 toward the first pipe T1.

[0044] At this point, the movable stopper 35 has not yet come into contact with the fixed stopper 55, so the downward rotation of the rotor 30 and the valve shaft 21 is not stopped, and pulse power supply is continued until the coil spring 24 is compressed by a predetermined amount. As a result, the needle valve 25 is restrained from rotating while remaining seated on the valve seat 11k, while the rotor 30, the valve shaft 21, the valve holder 23, etc. continue to rotate and downward.

[0045] At this time, the valve stem 21 and the valve holder 23 move downward relative to the seated needle valve 25, so that the coil spring 24 is compressed, thereby absorbing the downward force of the valve stem 21 and the valve holder 23. Thereafter, when the amount of compression of the coil spring 24 reaches a predetermined amount, the movable stopper 35 abuts against and is locked by the fixed stopper 55, the rotor 30 and the valve stem 21 reach their lowest positions, and the descent of the rotor 30 and the valve stem 21 is forcibly stopped even if pulse power supply to the stator continues.

[0046] In this way, even after the needle valve 25 is seated on the valve seat 11k and the orifice is closed, the rotor 30, the valve shaft 21, and the valve holder 23 continue to rotate downward, compressing the coil spring 24, until the movable stopper 35 reaches the control origin position where it abuts against and is locked against the fixed stopper 55. Therefore, the needle valve 25 is strongly pressed against the valve seat 11k by the biasing force of the coil spring 24, and refrigerant leakage, etc. can be reliably prevented.

[0047] On the other hand, when a pulse current of reverse polarity is supplied from the control origin position to the stator, the rotor 30 and the valve shaft 21 are rotated in the direction opposite to that when the valve is closed, and the rotor 30, the valve shaft 21, the valve holder 23, and the valve opening direction movable stopper 36 are rotated and raised by the screw feed mechanism consisting of the female screw hole 15c and the male screw portion 21b. As a result, the pressing force against 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, and flows to the first pipe T1 through the cylindrical hole 11i.

[0048] In this case, the lift amount of the needle valve 25 is determined according to the pulse power supply to the stator, so that the flow rate of the refrigerant can be controlled. By continuing the pulse power supply, the needle valve 25 will finally be fully opened. If the pulse power supply is continued, the movable stopper 36 will come into contact with and be locked by the valve opening direction fixed stopper 56, thereby forcibly stopping the rotation and ascent of the rotor 30, the valve shaft 21, and the valve holder 23.

[0049] According to this embodiment, when the valve is opened, the refrigerant passes through the gap between the conical portion 25d and the valve seat 11k and enters the cylindrical hole 11i of the valve seat member 11, the direction of the flow is changed by contacting the bottom wall 11h, and flows out of the valve seat member 11 through the cylindrical straightening holes 11j1, 11j2, 11j3, 11j4. At this time, since the central axes X1, X2, X3, X4 of the straightening holes 11j1, 11j2, 11j3, 11j4 are in a twisted relationship with the axis L, the refrigerant closer to the inner circumferential surface of the cylindrical hole 11i is supplied to each straightening hole more quickly than the refrigerant near the axis L in the cylindrical hole 11i.

[0050] In addition, since the central axes X1, X2, X3, and X4 of the flow straightening holes 11j1, 11j2, 11j3, and 11j4 are shifted toward the inner circumference of the cylindrical hole 11i with the same arrangement relationship with respect to the axis L, a swirling flow RF is generated in the refrigerant passing through the cylindrical hole 11i by being discharged from the flow straightening holes 11j1, 11j2, 11j3, and 11j4, as indicated by the arrows in FIG. 2.

[0051] When the valve is opened, the refrigerant passing through the orifice between the conical portion 25d and the valve seat 11k is often in a gas-liquid mixed state. When such a refrigerant passes through a narrow orifice, sound is generated due to the alternating passage of gas and liquid. If turbulence occurs in the cylindrical hole 11i, this may cause irregular changes in the sound, which may be recognized by the user as noise. In contrast, according to this embodiment, by creating a swirling flow RF in the cylindrical hole 11i, the generation of turbulence that generates a large number of small vortices is suppressed, and a stable state can be maintained in the cylindrical hole 11i. Therefore, the sound generated when the refrigerant in the gas-liquid phase passes through the orifice can be equalized, thereby suppressing the user from recognizing it as noise.

[0052] In addition, when a swirling flow RF is created in the cylindrical hole 11i, the liquid phase refrigerant, which has a high specific gravity, tends to collect on the outside due to centrifugal force, and the gas phase refrigerant, which has a low specific gravity, tends to collect in the center, thereby maintaining the refrigerant in a more stable state.

[0053] Furthermore, compared to the case where turbulent flow occurs within the cylindrical hole 11i, the creation of the swirling flow RF stabilizes the pressure applied to the needle valve 25, thereby suppressing vibration of the needle valve 25 and abnormal noise caused by the vibration.

[0054] Furthermore, by providing the valve seat member 11 having the flow straightening holes with a flow straightening effect, it becomes unnecessary to provide a separate flow straightening member, and the number of parts can be reduced.

[0055] In addition, according to this embodiment, the refrigerant that has passed through the cylindrical hole 11i, which is the orifice portion, is discharged from the flow straightening holes 11j1, 11j2, 11j3, and 11j4 so as to collide with the inner wall of the first pipe T1, so that the flow velocity of the refrigerant can be forcibly reduced and the refrigerant pressure can be restored before turbulence occurs, thereby suppressing the generation of bubbles that cause noise.

[0056] Furthermore, the refrigerant flowing out from the straightening holes 11j1, 11j2, 11j3, and 11j4 is also a swirling flow, and flows downstream while swirling along the inner wall of the first pipe T1. At this time, the liquid-phase refrigerant, which has a high specific gravity, tends to collect on the inner wall side of the first pipe T1 due to centrifugal force, and the gas-phase refrigerant, which has a low specific gravity, tends to collect on the center side of the first pipe T1. This makes it possible to maintain the refrigerant in a more stable state and reduce abnormal noise compared to a case without a swirling flow.

[0057] When the refrigerant flows from the first pipe T1 to the second pipe T2, the refrigerant that has entered the valve seat member 11 from the first pipe T1 has its flow direction changed by the flow straightening holes 11j1, 11j2, 11j3, and 11j4 to become a swirling flow, and does not flow straight along the axial direction to the orifice. Therefore, the refrigerant becomes stable when passing through the orifice, and the axial component of the flow velocity becomes small, thereby suppressing vibration of the needle valve 25 when the valve is opened.

[0058] [Second embodiment] FIG. 5 is a vertical cross-sectional view of a valve seat member 11A that can be used in a motor-operated valve according to a second embodiment. FIG. 6 is a bottom view of the valve seat member 11A 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 a duplicated description will be omitted. In addition, the configuration of the valve seat member 11A other than the straightening hole is the same as that of the valve seat member 11 according to the first embodiment, so the same reference numerals are used and a duplicated description will be omitted. In the following embodiments, a swirling flow of the refrigerant can be created in the downstream area of ​​the orifice portion and the straightening hole as in the first embodiment.

[0059] The valve seat member 11A of this embodiment is different from the valve seat member 11 shown in Fig. 4 in that there are two straightening holes. More specifically, two straightening holes 11Aj1, 11Aj2 extending obliquely outward from the outer periphery of the lower end of the cylindrical hole 11i are formed in opposite directions by branching in the circumferential direction, and the outer end of each straightening hole is located on the outer periphery of the truncated cone portion 11f. The central axes X1, X2 of the straightening holes 11Aj1, 11Aj2 intersect the cylindrical hole 11i, but are in a twisted relationship with respect to the axis L, that is, do not intersect spatially with the axis L. This embodiment can also achieve the same effects as the first embodiment.

[0060] [Third embodiment] Fig. 7 is a vertical cross-sectional view of a valve seat member 11B that can be used in a motor-operated valve according to a third embodiment. Fig. 8 is a bottom view of the valve seat member 11B 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 a duplicated description will be omitted. In addition, the configuration of the valve seat member 11B other than the flow straightening hole is the same as that of the valve seat member 11 according to the first embodiment, so the same reference numerals are used and a duplicated description will be omitted.

[0061] The valve seat member 11B of this embodiment is different from the valve seat member 11 shown in Fig. 4 in that it has three straightening holes. More specifically, the straightening holes 11Bj1, 11Bj2, and 11Bj3 extending obliquely outward from the outer periphery of the lower end of the cylindrical hole 11i are branched in the circumferential direction and formed at equal intervals, and the outer end of each straightening hole is located on the outer periphery of the truncated cone portion 11f. The central axes X1, X2, and X3 of the straightening holes 11Bj1, 11Bj2, and 11Bj3 intersect the cylindrical hole 11i, but are in a twisted relationship with respect to the axis L, that is, do not spatially intersect with the axis L. This embodiment can also achieve the same effects as the first embodiment.

[0062] [Fourth embodiment] 9 is a vertical cross-sectional view of a valve seat member 11C that can be used in a motor-operated valve according to a 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, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11C other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Cj1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0063] The valve seat member 11C of this embodiment differs from the valve seat member 11 shown in Fig. 2 mainly in that a tapered portion 11Cm, which is the lower end of the cylindrical hole 11Ci, is formed on the bottom wall 11Ch. A flow straightening hole 11Cj1 is in contact with a part of the tapered portion 11Cm. In this embodiment as well, a truncated cone portion 11Cf is disposed at the lower end of the inner cylindrical portion 11Ce. The central axis X1 of the flow straightening hole 11Cj1 intersects with the cylindrical hole 11Ci, but is in a twisted relationship with respect to the axis L, i.e., does not intersect with the axis L spatially.

[0064] When the valve is open, the refrigerant that passes through the orifice flows along the cylindrical hole 11Ci, which is the orifice portion, and reaches the tapered portion 11Cm. At least a part of the refrigerant is retained in the tapered portion 11Cm and then enters the flow straightening hole 11Cj1, which has the effect of making it easier to restore the refrigerant pressure. In addition, when the refrigerant passes through the edge portion of the tapered portion 11Cm, it also has the effect of dispersing air bubbles. The tapered portion 11Cm can be formed by transferring the shape of the tip of a cutting tool such as a drill when forming the cylindrical hole 11Ci.

[0065] [Fifth embodiment] 10 is a vertical cross-sectional view of a valve seat member 11D that can be used in a motor-operated valve according to a 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, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11D other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Dj1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0066] The valve seat member 11D of this embodiment is mainly different from the valve seat member 11 shown in Fig. 2 in that a communication opening 11Dm is formed from the middle position of the flow straightening hole 11Dj1, penetrating the bottom wall 11Dh parallel to the axis L, and the end portion is located on the top surface (lower surface) of the truncated cone portion 11Df. The inner diameter of the communication opening 11Dm is preferably ¼ or less of the inner diameter of the flow straightening hole 11Dj1. In this embodiment as well, the lower end of the inner cylindrical portion 11De is provided with the truncated cone portion 11Df. The central axis X1 of the flow straightening hole 11Dj1 intersects with the cylindrical hole 11Di, but is in a twisted relationship with respect to the axis L, i.e., does not intersect with the axis L spatially.

[0067] When the valve is opened, the refrigerant that passes through the orifice flows while swirling along the cylindrical hole 11Di, which is the orifice portion, and reaches the bottom wall 11Dh. From there, the refrigerant passes through the flow straightening hole 11Dj1 and flows out of the valve seat member 11D, but at that time, it may collide with the inner wall of the first pipe T1 and form a vortex. Such a vortex may hinder the recovery of the pressure of the refrigerant.

[0068] In contrast, according to the present embodiment, when the refrigerant passes through the upper end of the communication opening 11Dm, negative pressure is generated inside the communication opening 11Dm, so that the refrigerant is sucked up from the lower end of the communication opening 11Dm. This allows the vortex formed by the refrigerant colliding with the inner wall of the first pipe T1 to disappear quickly.

[0069] [Sixth embodiment] 11 is a vertical cross-sectional view of a valve seat member 11E that can be used in a motor-operated valve according to a sixth embodiment. The configuration of the motor-operated valve other than the valve seat member 11E is the same as that of the first embodiment, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11E other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Ej1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0070] The inner cylindrical portion 11Ee extending downward from the partition wall 11d is composed of an expanded diameter portion 11Ee1 on the partition wall 11d side and a reduced diameter portion 11Ee2 on the tip side having an outer diameter smaller than that of the expanded diameter portion 11Ee1. The first pipe T1 (FIG. 1) is fitted only into the expanded diameter portion 11Ee1.

[0071] The flow straightening hole 11Ej1 is formed so as to extend obliquely from the lower end of the cylindrical hole 11Ei formed inside the inner cylindrical portion 11Ee toward the valve seat 11k. The flow straightening hole 11Ej1 faces the inner wall of the first pipe T1 assembled to the valve seat member 11E. That is, the central axis X1 of the flow straightening hole 11Ej1 intersects with the inner wall of the first pipe T1 (see FIG. 1) but does not intersect with the axis L.

[0072] When the axis L is projected along the normal direction onto a plane that is parallel to the axis L and includes the central axis X1 of the flow straightening hole 11Ej1, the projected axis L and the central axis X1 intersect at an angle other than a right angle. The projected axis L toward the orifice side and the central axis X1 toward the tip side of the flow straightening hole form an acute angle on either side of the intersection.

[0073] In this embodiment as well, the length of the flow straightening hole 11Ej1 (the shortest length of the hole inner wall in the axial direction) is longer than the inner diameter of the flow straightening hole 11Ej1 and longer than the inner circumferential radius of the cylindrical hole 11Ei. The total flow path cross-sectional area of ​​the four flow straightening holes is larger than the orifice cross-sectional area at the maximum valve opening. The flow path cross-sectional area of ​​the cylindrical hole 11Ei is equal to or larger than the orifice cross-sectional area at the maximum valve opening. It is preferable that the total flow path cross-sectional area of ​​the flow straightening holes is larger than the flow path cross-sectional area of ​​the cylindrical hole 11Ei.

[0074] When the valve is open, the refrigerant passes through the orifice, swirls along the cylindrical hole 11Ei, which is the orifice portion, and reaches the bottom wall 11Eh, where the flow direction of the refrigerant is bent at an acute angle, passes through the flow straightening hole 11Ej1, and flows out of the valve seat member 11E.

[0075] Since there is a gap between the first pipe T1 and the reduced diameter portion 11Ee2, the refrigerant flowing out from the reduced diameter portion 11Ee2 hits the inner wall of the first pipe T1 and passes through the gap between the first pipe T1 and the reduced diameter portion 11Ee2 and flows downward. At this time, the flow speed of the refrigerant flowing out from between the first pipe T1 and the reduced diameter portion 11Ee2 is slower than the flow speed of the refrigerant passing through the orifice cross-sectional area when the valve is fully open.

[0076] [Seventh embodiment] Fig. 12 is a vertical cross-sectional view of a valve seat member 11F that can be used in a motor-operated valve according to a seventh embodiment. Fig. 13 is a bottom view of the valve seat member 11F 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 a duplicated description will be omitted. In addition, the configuration of the valve seat member 11F other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, so the same reference numerals are used and a duplicated description will be omitted.

[0077] The valve seat member 11F of this embodiment differs mainly in the shapes of the inner cylindrical portion 11Fe and the flow straightening holes 11Fj.

[0078] The inner cylindrical portion 11Fe extending downward from the partition wall portion 11d is composed of an expanded diameter portion 11Fe1 on the partition wall portion 11d side and a reduced diameter portion 11Fe2 on the tip side having an outer diameter smaller than that of the expanded diameter portion 11Fe1. The first pipe T1 (FIG. 1) is fitted only into the expanded diameter portion 11Fe1.

[0079] The flow straightening holes 11Fj are formed to extend radially outward from the lower end of the cylindrical hole 11Fi formed inside the inner cylindrical portion 11Fe. The central axis X1 of the flow straightening holes 11Fj intersects with the cylindrical hole 11Fi, but is in a twisted relationship with respect to the axis L, i.e., does not intersect spatially with the axis L. When the axis L is projected along the normal direction onto a plane that is parallel to the axis L and includes the central axis X1 of the flow straightening holes 11Fj, the projected axis L and the central axis X1 are perpendicular to each other. The flow straightening holes 11Fj face the inner wall of the first pipe T1 assembled to the valve seat member 11F.

[0080] In this embodiment, the length of the flow straightening hole 11Fj is preferably longer than the inner diameter of the flow straightening hole 11Fj and longer than the inner circumferential radius of the cylindrical hole 11Fi. The flow passage cross-sectional area of ​​the flow straightening hole 11Fj is larger than the orifice cross-sectional area at the maximum valve opening. The minimum flow passage cross-sectional area of ​​the cylindrical hole 11Fi is equal to or larger than the orifice cross-sectional area at the maximum valve opening. The flow passage cross-sectional area of ​​the flow straightening hole 11Fj is preferably larger than the flow passage cross-sectional area of ​​the cylindrical hole 11Fi.

[0081] When the valve is open, the refrigerant passes through the orifice, swirling along the cylindrical hole 11Fi which is the orifice portion, and reaches the bottom wall 11Fh, where the flow direction of the refrigerant is bent at a substantially right angle, passes through the flow straightening holes 11Fj, and flows out of the valve seat member 11F.

[0082] Since there is a gap between the first pipe T1 and the reduced diameter portion 11Fe2, the refrigerant flowing out from the reduced diameter portion 11Fe2 hits the inner wall of the first pipe T1 and passes through the gap between the first pipe T1 and the reduced diameter portion 11Fe2 and flows downward. At this time, the flow speed of the refrigerant flowing out from between the first pipe T1 and the reduced diameter portion 11Fe2 is slower than the flow speed of the refrigerant passing through the orifice cross-sectional area when the valve is fully open.

[0083] [Eighth embodiment] Fig. 14 is a vertical cross-sectional view of a valve seat member 11G that can be used in a motor-operated valve according to an eighth embodiment. Fig. 15 is a bottom view of the valve seat member 11G 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 a duplicated description will be omitted. In addition, the configuration of the valve seat member 11G other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, so the same reference numerals are used and a duplicated description will be omitted.

[0084] A valve seat member 11G of this embodiment differs from the valve seat member 11F shown in FIGS. 12 and 13 mainly in that a tapered portion 11Gm is formed at the inner end of the flow straightening hole 11Gj.

[0085] When the valve is open, the refrigerant that passes through the orifice flows while swirling along the cylindrical hole 11Gi, which is the orifice portion, and reaches the tapered portion 11Gm. At least a part of the refrigerant is retained in the tapered portion 11Gm and then enters the flow straightening hole 11Gj, which has the effect of making it easier to recover the refrigerant pressure. In addition, when the refrigerant passes through the edge portion of the tapered portion 11Gm, it also has the effect of dispersing air bubbles. The tapered portion 11Gm can be formed by transferring the shape of the tip of a cutting tool such as a drill when forming the flow straightening hole 11Gj.

[0086] [Ninth embodiment] 16 is a vertical cross-sectional view of a valve seat member 11H that can be used in a motor-operated valve according to a ninth embodiment. The configuration of the motor-operated valve other than the valve seat member 11H is the same as that of the first embodiment, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11H other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Hj1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0087] The cylindrical hole 11Hi has a first hole 11Hi1 disposed below the valve seat 11k, a second hole 11Hi2 having a larger diameter than the first hole 11Hi1, and a third hole 11Hi3 having a larger diameter than the second hole 11Hi2. The first hole 11Hi1 and the second hole 11Hi2 are connected by a first tapered portion 11Hi4, and the second hole 11Hi2 and the third hole 11Hi3 are connected by a second tapered portion 11Hi5. ​​The flow straightening hole 11Hj1 communicates with the lower end of the third hole 11Hi3 (and the second tapered portion 11Hi5). The cylindrical hole 11Hi can be formed by machining using, for example, an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. The flow passage cross-sectional area of ​​the first hole 11Hi1 is equal to or larger than the orifice cross-sectional area at the maximum valve opening. It is preferable that the total flow passage cross-sectional area of ​​the flow straightening holes is larger than the flow passage cross-sectional area of ​​the first hole 11Hi1. The central axis X1 of the flow straightening hole 11Hj1 intersects with the cylindrical hole 11Hi, but is in a skewed relationship with respect to the axis L; that is, it does not intersect with the axis L spatially.

[0088] When the valve is open, the refrigerant that passes through the orifice flows in a swirling manner along the first hole 11Hi1, the first tapered portion 11Hi4, the second hole 11Hi2, the second tapered portion 11Hi5, and the third hole 11Hi3, and reaches the bottom wall 11Hh. At this time, the flow path cross-sectional area expands in three stages from the orifice to the bottom wall 11Hh. This allows the refrigerant pressure to be gradually restored.

[0089] Furthermore, the refrigerant flows out of the valve seat member 11H through the straightening hole 11Hj1 facing diagonally downward and hits the inner wall of the first pipe T1, forcibly reducing the flow rate of the refrigerant and allowing the refrigerant pressure to be restored before turbulence occurs.

[0090] The total cross-sectional area of ​​the four straightening holes (11Hj1) is preferably larger than the cross-sectional area of ​​the first hole 11Hi1. Furthermore, the total cross-sectional area of ​​the four straightening holes (11Hj1) is more preferably smaller than the cross-sectional area of ​​the third hole 11Hi3.

[0091] [Tenth embodiment] 17 is a longitudinal sectional view of a valve seat member 11I that can be used in a motor-operated valve according to a 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, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11I other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Ij1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0092] In this embodiment as well, the central axis X1 of the flow straightening hole 11Ij1 intersects with the inner wall of the first pipe T1 (see FIG. 1), but does not intersect with the axis L.

[0093] The cylindrical hole 11Ii has a first hole 11Ii1 disposed below the valve seat 11k and a second hole 11Ii2 having a larger diameter than the first hole 11Ii1. The first hole 11Ii1 and the second hole 11Ii2 are connected by a tapered portion 11Ii3. The lower end of the second hole 11Ii2 is connected to the flow straightening hole 11Ij1. The cylindrical hole 11Ii can be formed by machining using, for example, an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. The flow passage cross-sectional area of ​​the first hole 11Ii1 is equal to or larger than the orifice cross-sectional area when the valve is fully open. It is preferable that the total flow passage cross-sectional area of ​​the flow straightening holes is larger than the flow passage cross-sectional area of ​​the first hole 11Ii1.

[0094] When the valve is open, the refrigerant that passes through the orifice flows through the first hole 11Ii1, the tapered portion 11Ii3, and the second hole 11Ii2 while swirling, and reaches the bottom wall 11Ih. At this time, the flow path cross-sectional area expands in two stages from the orifice to the bottom wall 11Ih. This allows the refrigerant pressure to gradually recover.

[0095] Furthermore, the refrigerant passes through the straightening hole 11Ij1 facing diagonally downward and flows out of the valve seat member 11I, where it hits the inner wall of the first pipe T1, forcibly reducing the flow velocity of the refrigerant and allowing the refrigerant pressure to be restored before turbulence occurs.

[0096] [Eleventh embodiment] 18 is a vertical cross-sectional view of a valve seat member 11J that can be used in a motor-operated valve according to an eleventh embodiment. The configuration of the motor-operated valve other than the valve seat member 11J is the same as that of the first embodiment, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11J other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Jj1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0097] The cylindrical hole 11Ji has a first hole 11Ji1 disposed below the valve seat 11k and a second hole 11Ji2 having a larger diameter than the first hole 11Ji1. The first hole 11Ji1 and the second hole 11Ji2 are connected by a tapered portion 11Ji3. The lower end of the second hole 11Ji2 is connected to the flow straightening hole 11Jj1. The cylindrical hole 11Ji can be formed by machining using, for example, an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. The flow passage cross-sectional area of ​​the first hole 11Ji1 is equal to or larger than the orifice cross-sectional area at the maximum opening. The total flow passage cross-sectional area of ​​the flow straightening holes is preferably larger than the flow passage cross-sectional area of ​​the first hole 11Ji1. The central axis X1 of the flow straightening hole 11Jj1 intersects the cylindrical hole 11Ji, but is in a twisted relationship with respect to the axis L, that is, does not intersect spatially with the axis L.

[0098] The central hole 11Jn connected to the lower end of the cylindrical hole 11Ji is coaxial with the cylindrical hole 11Ji and has an inner diameter smaller than the inner diameters of the cylindrical hole 11Ji and the flow straightening hole 11Jj1.

[0099] When the valve is open, the refrigerant that passes through the orifice flows in a swirling manner along the first hole 11Ji1, the tapered portion 11Ji3, and the second hole 11Ji2, and reaches the bottom wall 11Jh. At this time, the flow path cross-sectional area expands in two stages from the orifice to the bottom wall 11Jh. This allows the refrigerant pressure to be gradually restored.

[0100] A part of the refrigerant that reaches the bottom wall 11Jh passes through the flow straightening holes 11Jj1 and flows out of the valve seat member 11J and collides with the first pipe T1, which may form a vortex. On the other hand, the rest of the refrigerant that reaches the bottom wall 11Jh passes straight through the central hole 11Jn and flows out of the valve seat member 11J, which has the effect of eliminating the vortex that has formed on the inner wall of the first pipe T1. This allows the refrigerant pressure to be quickly restored.

[0101] [Twelfth embodiment] 19 is a vertical cross-sectional view of a valve seat member 11K that can be used in a motor-operated valve according to a twelfth embodiment. The configuration of the motor-operated valve other than the valve seat member 11K is the same as that of the first embodiment, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11K other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Kj1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0102] In this embodiment as well, the central axis X1 of the flow straightening hole 11Kj1 intersects with the inner wall of the first pipe T1 (see FIG. 1), but does not intersect with the axis L.

[0103] In this embodiment, the flow straightening hole 11Kj1 is connected between the lower end and the upper end of the cylindrical hole 11Ki, so that a refrigerant retention portion 11Kp is formed in the bottom wall 11Kh at the lower end of the cylindrical hole 11Ki up to the connecting portion with the flow straightening hole 11Kj1.

[0104] When the valve is open, the refrigerant that passes through the orifice flows while swirling along the cylindrical hole 11Ki, which is the orifice portion, and reaches the retention portion 11Kp in the bottom wall 11Kh. Here, the refrigerant flow makes a U-turn and passes through the flow straightening hole 11Kj1 to flow out of the valve seat member 11K, at which point the pressure of the refrigerant is restored and the number of air bubbles can be reduced.

[0105] [Thirteenth embodiment] 20 is a vertical cross-sectional view of a valve seat member 11L that can be used in a motor-operated valve according to a thirteenth embodiment. The configuration of the motor-operated valve other than the valve seat member 11L is the same as that of the first embodiment, and therefore a duplicated description will be omitted. Also, the configuration of the valve seat member 11L other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment as well, four straightening holes (two in the figure) are provided.

[0106] The valve seat member 11L of this embodiment differs from the twelfth embodiment in that the connection position of the flow straightening hole 11Lj3 facing the flow straightening hole 11Lj1 to the cylindrical hole 11Li is shifted (displaced) by a distance σ downward in the axial direction. The distance σ is preferably 0.2φ to 0.8φ, where φ is the inner diameter of the flow straightening hole. This makes it possible to reduce the flow velocity of the refrigerant passing through the cylindrical hole 11Li while swirling. Note that for each flow straightening hole, the connection positions of the adjacent flow straightening holes to the cylindrical hole 11Li may be shifted by an equal distance in the axial direction, or two pairs of flow straightening holes may be shifted in the axial direction at a time.

[0107] [Fourteenth embodiment] 21 is a vertical cross-sectional view of a valve seat member 11M that can be used in a motor-operated valve according to a fourteenth embodiment. The configuration of the motor-operated valve other than the valve seat member 11M is the same as that of the first embodiment, and therefore a duplicated description will be omitted. Also, the configuration of the valve seat member 11M other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Mj1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0108] In this embodiment as well, the central axis X1 of the flow straightening hole 11Mj1 intersects with the inner wall of the first pipe T1 (see FIG. 1), but does not intersect with the axis L.

[0109] The inner cylindrical portion 11Me extending downward from the partition wall 11d is composed of an expanded diameter portion 11Me1 on the partition wall 11d side and a reduced diameter portion 11Me2 on the tip side having a smaller outer diameter than the expanded diameter portion 11Me1. A truncated cone portion 11Mf is formed at the lower end of the reduced diameter portion 11Me2. The first pipe T1 (FIG. 1) is fitted only into the expanded diameter portion 11Me1.

[0110] A flow straightening hole 11Mj1 is formed so as to extend obliquely downward from the lower end of a cylindrical hole 11Mi formed inside the inner cylindrical portion 11Me. A communication opening 11Mn is formed so as to extend obliquely from the middle position of the flow straightening hole 11Mj1 toward the partition wall portion 11d. The inner diameter of the communication opening 11Mn is preferably ¼ or less of the inner diameter of the flow straightening hole Mj1.

[0111] When the valve is open, the refrigerant that passes through the orifice flows while swirling along the cylindrical hole 11Mi, which is the orifice portion, and reaches the bottom wall 11Mh. From there, the refrigerant passes through the flow straightening hole 11Mj1 and flows out of the valve seat member 11M, but in that case, it may collide with the inner wall of the first pipe T1 and form a vortex. Such a vortex may hinder the recovery of the pressure of the refrigerant.

[0112] In contrast, according to the present embodiment, when the refrigerant passes through the lower end of the communication opening 11Mn, negative pressure is generated inside the communication opening 11Mn, and the refrigerant is sucked in from the upper end of the communication opening 11Mn, whereby the eddy current formed when the refrigerant collides with the inner wall of the first pipe T1 can be quickly eliminated.

[0113] [Fifteenth embodiment] 22 is a vertical cross-sectional view of a valve seat member 11N that can be used in a motor-operated valve according to a fifteenth embodiment. The configuration of the motor-operated valve other than the valve seat member 11N is the same as that of the first embodiment, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11N other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configurations of the flow straightening holes 11Nj1, 11Nj2, and 11Nj3 will be described as representatives of the twelve flow straightening holes, but the other flow straightening holes have the same configuration.

[0114] In this embodiment, the inner cylindrical portion 11Ne is formed longer than in the first embodiment. The inner cylindrical portion 11Ne is composed of an expanded diameter portion 11Ne1 on the partition wall portion 11d side and a reduced diameter portion 11Ne2 on the tip side having an outer diameter smaller than that of the expanded diameter portion 11Ne1. The first pipe T1 (FIG. 1) is fitted only to the expanded diameter portion 11Ne1. In the inner cylindrical portion 11Ne, the flow straightening holes 11Nj1, 11Nj2, and 11Nj3 are arranged in a row in a position where they overlap vertically in the direction along the axis L. The other flow straightening holes are also similarly arranged in three rows of three. The central axes X1, X2, and X3 of the flow straightening holes 11Nj1, 11Nj2, and 11Nj3 pass through the same plane parallel to the axis L and intersect the inner wall of the first pipe T1 (see FIG. 1), but do not intersect the axis L.

[0115] In this embodiment, the lowermost straightening hole 11Nj3 is connected to the cylindrical hole 11Ni above the lower end of the cylindrical hole 11Ni, but may be connected to the lower end of the cylindrical hole 11Ni.

[0116] According to this embodiment, by providing four sets of straightening holes arranged in three rows, a stronger swirling flow can be created inside the cylindrical hole 11Ni. Note that any number of sets of straightening holes in any number of rows can be provided.

[0117] [Sixteenth embodiment] 23 is a longitudinal sectional view of a valve seat member 11O that can be used in a motor-operated valve according to a sixteenth embodiment. The configuration of the motor-operated valve other than the valve seat member 11O is the same as that of the first embodiment, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11O other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configurations of the flow straightening holes 11Oj1, 11Oj2, 11Oj3 and the flow straightening holes 11Oj4, 11Oj5, 11Oj6 will be described as representatives of the twelve flow straightening holes, but the other flow straightening holes have the same configuration.

[0118] The valve seat member 11O of this embodiment is different from the fifteenth embodiment in that the connection position of the flow straightening hole 11Oj4 facing the flow straightening hole 11Oj1 to the cylindrical hole 11Oi is shifted downward in the axial direction by a distance σ, the connection position of the flow straightening hole 11Oj5 facing the flow straightening hole 11Oj2 to the cylindrical hole 11Oi is shifted downward in the axial direction by a distance σ, and the connection position of the flow straightening hole 11Oj6 facing the flow straightening hole 11Oj3 to the cylindrical hole 11Oi is shifted downward in the axial direction by a distance σ. This makes it possible to reduce the flow velocity of the refrigerant passing through the cylindrical hole 11Oi while swirling. Note that the connection positions of the adjacent flow straightening holes to the cylindrical hole 11Oi may be shifted in the axial direction by the same amount for each flow straightening hole.

[0119] [Seventeenth embodiment] 24 is a vertical cross-sectional view of a valve seat member 11P that can be used in a motor-operated valve according to a seventeenth embodiment. The configuration of the motor-operated valve other than the valve seat member 11P is the same as that of the first embodiment, and therefore a duplicated description will be omitted. In addition, the configuration of the valve seat member 11P other than the inner cylindrical portion is the same as that of the valve seat member 11 according to the first embodiment, and therefore the same reference numerals are used and a duplicated description will be omitted. In this embodiment, the configuration of the flow straightening hole 11Pj1 will be described as a representative of the four flow straightening holes, but the other flow straightening holes have the same configuration.

[0120] In this embodiment, the cylindrical hole 11Pi has an upper cylindrical hole 11Pi1 connected to the orifice and a lower cylindrical hole 11Pi2 having a smaller diameter than the upper cylindrical hole 11Pi1. A spiral groove 11Pp is formed as a swirling flow generating structure on at least a part of the inner circumference of the lower cylindrical hole 11Pi2.

[0121] The spiral direction of the spiral groove 11Pp is determined according to the positional relationship between the axis L and the flow straightening hole 11Pj1. More specifically, when the axis L and the flow straightening hole 11Pj1 are in the positional relationship shown in FIG. 4, the refrigerant flowing along the cylindrical hole 11Pi swirls counterclockwise along the direction of travel. In this case, the spiral groove 11Pp preferably has a left-handed spiral direction toward the bottom end of the cylindrical hole 11Pi to strengthen the swirl flow of the refrigerant. Note that a cylinder with a spiral groove formed on its inner circumference may be fitted into the cylindrical hole 11Pi.

[0122] [Variations] 25 is a diagram showing a configuration in which a valve seat member 11 and a porous filter FT that can be used in a motor-operated valve according to a modified example of this embodiment are combined, with the left half being a vertical cross-sectional view and the right half being a side view. The configuration other than the porous filter FT is the same as that of the first embodiment, so duplicated explanations will be omitted.

[0123] A metal or resin porous filter FT is disposed around the inner cylindrical portion 11e of the valve seat member 11 so as to cover the area from the position indicated by the dotted line to below the truncated cone portion 11f. The porous filter FT is formed into a cylindrical shape from, for example, foamed metal, a mesh material, or punched metal, and is wrapped around the outer periphery of the inner cylindrical portion 11e so as to cover the outer ends of the flow straightening holes 11j1, etc.

[0124] The refrigerant flowing out from the straightening holes 11j1 etc. passes through the porous filter FT, whereby the bubbles are broken down into finer particles, which is further effective in reducing noise. The valve seat member combined with the porous filter FT is not limited to that in the first embodiment, and may be combined with any of the other embodiments. [Explanation of symbols]

[0125] 1 Motor-operated valve 10 Valve body 11~11O Valve seat member 11k valve seat 15 Guide stem 21 Valve stem 23 Valve holder 24 Coil spring 25 Needle valve 26 Spring support member 27 Annular member 29 Valve chamber 30 rotors 35 Movable stopper for closing valve direction 36 Movable stopper for opening direction 55 Fixed stopper for closing direction 56 Valve opening direction fixed stopper FT Porous Filter

Claims

1. A valve body having a valve chamber; a valve seat member provided on the valve body and having a valve seat; a valve body that is disposed in the valve chamber and is movable up and down in a direction toward or away from the valve seat, the valve seat member includes an orifice portion adjacent to the valve seat and a flow straightening hole communicating with the orifice portion, The valve seat member has a truncated cone portion, and an outlet of the flow straightening hole is formed on an outer circumferential surface of the truncated cone portion, a central axis of the flow straightening hole is not parallel to and does not intersect with the axis of the orifice portion, and passes between an inner circumferential surface of the orifice portion and the axis of the orifice portion, when the axis of the orifice portion is projected along a normal direction of a plane including the central axis of the flow straightening hole and parallel to the axis of the orifice portion, the central axis of the flow straightening hole intersects with the projected axis of the orifice portion, and an obtuse angle is formed between the projected axis toward the valve seat side and the central axis toward the tip side of the flow straightening hole, with the intersection therebetween. A motor-operated valve.

2. The minimum distance between the central axis of the flow straightening hole and the axis of the orifice portion is 0.3 to 0.7 times the inner diameter of the flow straightening hole.

2. The motor-operated valve according to claim 1.

3. The flow straightening hole is branched into a plurality of holes from the orifice portion.

3. The motor-operated valve according to claim 1 or 2.

4. The valve seat member has the orifice portion formed therein and includes a cylindrical portion that fits into a pipe. The motor-operated valve according to any one of claims 1 to 3.

5. A truncated cone portion is formed at an end of the cylindrical portion, and an outer end of the flow straightening hole is located on an outer circumferential surface of the truncated cone portion.

5. The motor-operated valve according to claim 4.

6. A tapered portion is formed at an inner end of the orifice portion. The motor-operated valve according to any one of claims 1 to 5.

7. a communication opening extending from the flow straightening hole to an outside of the valve seat member, the communication opening having an inner diameter smaller than an inner diameter of the flow straightening hole; The motor-operated valve according to any one of claims 1 to 6.

8. The orifice portion has, in order from the valve seat side, a first hole and a second hole having a larger diameter than the first hole. The motor-operated valve according to any one of claims 1 to 7.

9. 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 8.

10. A plurality of the straightening holes are formed along a circumferential direction of the orifice portion, and one of the straightening holes is offset in an axial direction of the orifice portion with respect to another of the straightening holes adjacent thereto in the circumferential direction. The motor-operated valve according to any one of claims 1 to 9.

11. A plurality of the flow straightening holes are arranged along the axial direction of the orifice portion. The motor-operated valve according to any one of claims 1 to 10.

12. A swirling flow generating structure is disposed inside the orifice portion. The motor-operated valve according to any one of claims 1 to 11.

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