Motorized valve

Abstract

Provided is an electric valve that can suppress costs and further reduce noise. The electric valve has a valve body that has a valve chamber; a valve seat member that is attached to the valve body and has a valve seat; and a valve core that is disposed in the valve chamber and can be raised and lowered in a direction that approaches or departs from the valve seat. The valve seat member can be connected to a pipe and has a throttle hole portion that is adjacent to the valve seat and a straightening hole that is connected to the throttle hole portion. A central axis of the straightening hole intersects an inner wall of the pipe.

Description

Technical Field

[0001] This invention relates to an electric valve. Background Technology

[0002] Electric valves used as flow control valves in refrigeration cycles have a threaded mechanism that engages the external thread of a valve shaft driven by an electric motor with an internal threaded hole in the valve body. This threaded 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 component (perforated plate) with multiple small holes for throttling and bubble subdivision is installed on the main body, allowing refrigerant to pass through. Based on this thin plate component, it can perform the functions of rectifying and throttling refrigerant flowing in a two-phase flow state, and subdividing and differentiating bubbles in the two-phase flow refrigerant, effectively reducing the noise caused by bubbles during refrigerant passage.

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 2007-107623

[0007] The technical problem that the invention aims to solve

[0008] In a refrigeration cycle, the refrigerant typically flows from the piping into the valve body of the electric valve in a gas-liquid two-phase flow state, thus inherently containing air bubbles. Furthermore, as the refrigerant passes through the orifice, a pressure drop occurs, causing some of the refrigerant to vaporize and generate bubbles. The bursting of these bubbles produces noise.

[0009] According to the electric valve in Patent Document 1, the noise caused by refrigerant passing through due to air bubbles can be reduced, but there is still room for further noise reduction.

[0010] The inventors of this application discovered that in the electric valve of Patent Document 1, turbulence and noise are generated when the refrigerant passing through the throttling orifice enters a larger diameter pipe through the small hole of the thin plate component during pressure recovery. Furthermore, the electric valve of Patent Document 1 requires a thin plate component, thus increasing the number of parts and complicating assembly. Summary of the Invention

[0011] Therefore, the object of the present invention is to provide an electric valve that can suppress costs and further reduce noise.

[0012] Technical means for solving technical problems

[0013] To solve the above-mentioned technical problems, the electric valve of the present invention has the following features:

[0014] Valve body, which includes a valve chamber;

[0015] A valve seat assembly, which is mounted on the valve body and has a valve seat; and

[0016] A valve core, which is disposed in the valve chamber and is capable of moving up and down in the direction of approaching or moving away from the valve seat.

[0017] The valve seat component is connectable to a piping system and includes a throttling orifice and a rectifying orifice. The throttling orifice is adjacent to the valve seat, and the rectifying orifice is connected to the throttling orifice.

[0018] The central axis of the rectifier orifice intersects the inner wall of the piping.

[0019] The effects of the invention

[0020] According to the present invention, it is possible to provide an electric valve that can suppress costs and further reduce noise. Attached Figure Description

[0021] Figure 1 This is a longitudinal sectional view showing the electric valve according to the first embodiment of the present invention.

[0022] Figure 2 This is a longitudinal sectional view of the valve seat component according to the first embodiment.

[0023] Figure 3 This is a perspective view of the valve seat component of the first embodiment, as seen from below.

[0024] Figure 4 This is a bottom view of the valve seat component according to the first embodiment.

[0025] Figure 5 This is a longitudinal sectional view of the valve seat component that can be used in the electric valve of the second embodiment.

[0026] Figure 6 This is a longitudinal sectional view of the valve seat component that can be used in the electric valve of the third embodiment.

[0027] Figure 7 This is a longitudinal sectional view of the valve seat component of the electric valve that can be used in the fourth embodiment.

[0028] Figure 8 This is a longitudinal sectional view of the valve seat component of the electric valve that can be used in the fifth embodiment.

[0029] Figure 9 This is a longitudinal sectional view of the valve seat component of the electric valve that can be used in the sixth embodiment.

[0030] Figure 10This is a longitudinal sectional view of the valve seat component of the electric valve that can be used in the seventh embodiment.

[0031] Figure 11 This is a longitudinal sectional view of the valve seat component of the electric valve that can be used in the eighth embodiment.

[0032] Figure 12 This is a longitudinal sectional view of the valve seat component of the electric valve that can be used in the ninth embodiment.

[0033] Figure 13 This is a longitudinal sectional view of the valve seat component of the electric valve that can be used in the tenth embodiment.

[0034] Figure 14 This is a longitudinal sectional view of the valve seat component of the electric valve that can be used in the eleventh embodiment.

[0035] Figure 15 This diagram shows the structure of the electric valve seat component and the porous filter combined in a modified example of this embodiment.

[0036] Symbol Explanation

[0037] 1 Electric valve

[0038] 10 Valve body

[0039] 11~11K Valve seat components

[0040] 11e valve seat

[0041] 15 Guide rods

[0042] 21 Valve shaft

[0043] 23 Valve retainer

[0044] 24 Coil Spring

[0045] 25 needle valve

[0046] 26 Spring support components

[0047] 27. Ring-shaped components

[0048] 29 Valve Chamber

[0049] 30 rotors

[0050] 35. Movable stop for valve closing direction

[0051] 36. A movable stop is used for the valve opening direction.

[0052] 55. Fixed stop for valve closing direction

[0053] 56. Fixed stop for valve opening direction

[0054] FT porous filter Detailed Implementation

[0055] Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

[0056] [First Implementation Method]

[0057] Figure 1 This is a longitudinal sectional view of the electric valve 1 according to the 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. Furthermore, "throttling orifice" refers to the gap between the needle valve and the valve seat when the valve is open; 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 "throttling cross-sectional area". "Throttling orifice portion" is the flow path from the valve seat to the downstream side and up to the boundary with the rectifier orifice. Furthermore, "flow path cross-sectional area" refers to the cross-sectional area of ​​the flow path orthogonal to the direction of refrigerant flow.

[0058] (Structure of a flow control valve)

[0059] The electric valve 1 comprises: a bottomed cylindrical valve body 10 with an open top; a topped cylindrical outer shell 45 sealed to the upper surface of the valve body 10 by welding or the like; a guide rod 15 fixed to the inner side of the valve body 10; a valve shaft 21 disposed on the inner side of the guide rod 15; and a rotor 30 connected and fixed to the valve shaft 21 in a manner that allows it to rotate integrally with the valve shaft 21. A stator, which is externally embedded in the outer periphery of the outer shell 45, is arranged around the rotor 30 to drive its rotation, but is not shown in the figure here. The rotor 30 and the stator constitute a stepper motor. The axis of the electric valve 1 is defined as L.

[0060] The valve body 10 is formed by continuously providing a hollow cylindrical portion 10a and a bottom wall portion 10b. The valve body 10 can be formed by stamping a sheet of SUS material, or it can be formed by pressing SUS material. The valve body 10 can be formed using materials other than SUS (stainless steel) (such as brass), and it can also be formed using processing methods other than stamping and pressing (such as machining).

[0061] In the bottom wall portion 10b, a circular opening 10d is formed in the center, and a valve seat component 11 is fixed in the opening 10d by brazing or the like.

[0062] Figure 2 This is a longitudinal sectional view of valve seat component 11. Figure 3 This is a perspective view of the valve seat component 11 as seen from below. Figure 4 This is a bottom view of valve seat component 11.

[0063] The generally cylindrical valve seat component 11 is formed by continuously arranging an upper cylindrical portion 11a, a middle cylindrical portion 11b with a diameter larger than that of the upper cylindrical portion 11a, a lower cylindrical portion 11c with a diameter larger than that of the middle cylindrical portion 11b, a partition portion 11d extending radially inward from near 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 portion 11d. The lower end of the inner cylindrical portion 11e has a frustoconical portion 11f.

[0064] 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 on the outside of the valve body 10. Furthermore, 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 circumference of the lower end of the lower cylindrical portion 11c. The first pipe T1 (enters the annular space SP) Figure 1 The end of the tube is inserted into the outer periphery of the inner cylindrical portion 11e and connected by brazing or the like. The stepped portion 11g serves as a storage area for solder when brazing the pipe T1.

[0065] A cylindrical hole 11i extending downward along axis L from the upper end of the inner cylindrical portion 11e to the bottom wall 11h is formed coaxially with axis L. Four rectifying holes 11j, branching outward obliquely from the lower outer circumference of the cylindrical hole 11i, are formed at equal intervals in the circumferential direction, with the outer end of each rectifying hole 11j located on the outer circumferential surface of the frustum-shaped portion 11f. Therefore, the rectifying holes 11j face the inner wall of the first pipe T1 mounted on the valve seat component 11. Specifically, when a cross-section of the rectifying hole 11j is projected along its central axis X, the projected image coincides with the inner wall of the first pipe T1. In other words, the central axis X of the rectifying hole 11j intersects the inner wall of the first pipe T1. The central axis X of the rectifying hole 11j intersects axis L at an angle θ greater than 0 degrees and less than 90 degrees (defined as the angle between axis L extending downward from the intersection with central axis X and central axis X, the same applies below). The number of rectifying orifices 11j can be two, three, or more, but they are preferably arranged at equal intervals in the circumferential direction. Cylindrical orifices 11i constitute throttling orifices. A valve seat 11k is formed on the inner circumference of the upper end of the inner cylindrical portion 11e. Furthermore, in a structure where the central axis X and axis L are arranged in a way that they do not intersect in space (forming a torsional relationship), the angle at which the central axis X intersects the axis L in a side view (view from the orthogonal direction of axis L) is taken as the intersection angle θ.

[0066] In this embodiment, the length of the rectifier orifice 11j is longer than its inner diameter and longer than the inner circumferential radius of the cylindrical orifice 11i. A cross-section obtained by cutting the electric valve 1 with a plane passing through axis L and central axis X (here, Figure 2In the diagram, the inner wall of the rectifier orifice 11j is represented as a pair of line segments separated by a central axis X, the central axis X of the rectifier orifice 11j being a straight line connecting one end of each line segment of the inner wall to the other. Figure 2 (The dashed line) PL1 and the straight line connecting the other ends to each other ( Figure 2 When the dashed line PL2 intersects at points PT1 and PT2, the length of the rectifier orifice 11j refers to the distance between those points PT1 and PT2.

[0067] Furthermore, the total flow path cross-sectional area of ​​the four rectifying orifices 11j is greater than the flow path cross-sectional area (i.e., throttling cross-sectional area) formed between the conical portion 25d and the valve seat 11k when the needle valve (valve core) 25 is at its maximum lift (maximum valve opening). Additionally, the flow path cross-sectional area of ​​the cylindrical orifice 11i is greater than or equal to the throttling cross-sectional area at maximum valve opening. Preferably, the total flow path cross-sectional area of ​​the rectifying orifices 11j is greater than the flow path cross-sectional area of ​​the cylindrical orifice 11i.

[0068] exist Figure 1 In the valve body 10, an inlet opening 10e is formed in the hollow cylindrical portion 10a. The end of the 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 set to O.

[0069] With the lower end of the outer casing 45 abutting against the upper end of the valve body 10, a flange-shaped disc 18 is fitted into the inner circumference of the lower end of the outer casing 45 and joined together by welding. Thus, the valve body 10 and the outer casing 45 are integrated in a sealed state.

[0070] The flanged disc 18 has multiple through holes (not shown) through which refrigerant can move between the valve body 10 side and the housing 45 side.

[0071] The resin guide rod 15, disposed inside the rotor 30, is continuously formed by a solid cylindrical body 15a and a hollow cylindrical portion 15b. The body 15a has an internally threaded hole 15c along the axis L. In addition, a movable stop member 35 for closing the valve is provided above the guide rod 15.

[0072] A flange-shaped disk 18, welded to the upper end of the valve body 10, is disposed on the outer periphery of the middle portion of the hollow cylindrical portion 15b. The guide rod 15 is fixed relative to the valve body 10 via the flange-shaped disk 18. A pressure equalization hole 15d is formed in the hollow cylindrical portion 15b.

[0073] Furthermore, to set the control origin position of the rotor 30 and valve shaft 21, a rectangular cross-section valve-closing direction fixing stop 55 is provided protruding upward on the upper surface of the main body 15a of the guide rod 15, and a rectangular cross-section valve-opening direction fixing stop 56 is provided protruding downward on the lower surface of the main body 15a of the guide rod 15. Here, the control origin position of the rotor 30 and valve shaft 21 refers to the position when the rotor 30 and valve shaft 21 reach their lowest descending position, where the movable valve-closing direction stop 35 abuts against the valve-closing direction fixing stop 55 and is locked in place.

[0074] The metal valve shaft 21 is formed by continuously and coaxially arranging the end 21a of the annular connector 32 that is externally embedded in the rotor 30, the external threaded portion 21b that is screwed into the internal threaded hole 15c, the flange-like portion 21c formed near the lower end, and the lower end connecting portion 21d.

[0075] A movable stop 35, fixed to the valve shaft 21 in the valve closing direction, is disposed near the upper end of the external thread portion 21b and is engaged with the lower surface of the upper wall of the rotor 30. A stop portion 35a with a rectangular cross-section is formed on the lower surface of the movable stop 35 in the valve closing direction.

[0076] Furthermore, a movable stop 36 for the valve opening direction is pressed into and fitted near the lower end of the external threaded portion 21b of the valve shaft 21, abutting against the upper surface of the flange-shaped portion 21c. A stop portion 36a with a rectangular cross-section is formed on the upper surface of the movable stop 36 for the valve opening direction. Here, the movable stop 36 for the valve opening direction is fixed to the valve shaft 21 by forming an internal thread on the inner circumference of the movable stop 36 for the valve opening direction and screwing it into the external threaded portion 21b.

[0077] Below the valve shaft 21, the valve retainer 23 is slidably fitted into the inner side of the hollow cylindrical portion 15b. The valve retainer 23 has a topped cylindrical shape that continuously connects the hollow cylindrical portion 23a and the upper wall 23b. A stepped opening 23c is formed in the center of the upper wall 23b, and the hollow cylindrical portion 23a has a connecting hole 23d. In the closed valve state, the open lower end of the hollow cylindrical portion 23a of the valve retainer 23 is positioned below the second piping T2 and is closed by a riveted annular member 27.

[0078] With the flange-like portion 21c of the valve shaft 21 abutting against the stepped portion of the stepped opening 23c, the lower connecting portion 21d penetrates through the stepped opening 23c. By riveting the lower connecting portion 21d in an enlarged manner, the valve shaft 21 and the valve retainer 23 are fixedly connected. A valve chamber 29 is defined between the valve body 10 and the valve retainer 23.

[0079] The needle valve 25 is configured to protrude from the valve holder 23 through the annular member 27. The needle valve 25 is formed by continuously arranging a cylindrical shaft portion 25a, a valve flange portion 25b, a valve cylinder portion 25c, a conical portion 25d that tapers downwards, and a plurality of conical tips 25e formed in stages. The cone angle (the angle intersecting the axis L) of the conical portion 25d is greater than the cone angle of the tips 25e connected to the conical portion 25d.

[0080] The annular component 31 is fitted onto the outer periphery of the shaft portion 25a by pressing or the like. The outer diameter of the annular component 31 is larger than the inner diameter of the annular component 27, thus preventing the needle valve 25 from falling off the valve holder 23. A washer 28 is provided between the annular component 31 and the annular component 27 to reduce friction when the annular component 31 and the annular component 27 rotate relative to each other.

[0081] A cylindrical spring support member 26 is disposed between the upper wall 23b of the valve retainer 23 and the needle valve 25. The spring support member 26 has a lower flange portion 26a. Furthermore, a helical spring 24 is disposed between the upper wall 23b and the lower flange portion 26a. The helical spring 24 exerts a force on the spring support member 26 downward relative to the valve retainer 23.

[0082] The conical portion 25d sits on the valve seat 11k of the valve seat component 11. When subjected to an upward reaction force, the spring support component 26, which is exerted upward force by the needle valve 25, abuts against the lower surface (or lower end connection portion 21d) of the upper wall 23b of the valve holder 23, thereby locking the needle valve 25 relative to the valve shaft 21 in the axial direction.

[0083] When the needle valve 25 is off the valve seat 11k (open valve state), the valve shaft 21, valve retainer 23, needle valve 25 and helical spring 24 are essentially integrated and rotate and move up and down relative to the guide rod 15.

[0084] (Action of the flow control valve)

[0085] The operation of electric valve 1 will be explained in detail.

[0086] Here, it is assumed that the refrigerant (fluid) enters the valve chamber 29 from the second pipe T2.

[0087] By pulse power supplied to the stator (not shown) from an external control device, the rotor 30 and valve shaft 21 are driven to rotate in one direction. Through a threaded feed mechanism consisting of an internal threaded hole 15c and an external threaded portion 21b, the valve shaft 21 and the valve closing direction are lowered while rotating by a movable stop 35, causing the needle valve 25 to sit on the valve seat 11k and close the throttling orifice. This cuts off the flow of refrigerant from the valve chamber 29 toward the first piping T1 side.

[0088] At this moment, the movable stop 35 has not yet come into contact with the fixed stop 55, and the rotation and descent of the rotor 30 and valve shaft 21 have not stopped. The pulse power supply continues until the helical spring 24 is compressed to a predetermined amount. As a result, the rotation of the needle valve 25 is stopped in the state of sitting on the valve seat 11k, while the rotor 30, valve shaft 21, valve retainer 23, etc. continue to rotate and descend.

[0089] At this time, as the valve shaft 21 and valve retainer 23 descend relative to the seated needle valve 25, the coil spring 24 is compressed, thereby absorbing the descending force of the valve shaft 21 and valve retainer 23. Then, when the compression of the coil spring 24 reaches a predetermined amount, the movable stop 35 abuts against the fixed stop 55 and locks in place, and the rotor 30 and valve shaft 21 reach their lowest descending position. Even if stator pulse power supply continues, the descent of the rotor 30 and valve shaft 21 is forcibly stopped.

[0090] In this way, even after the needle valve 25 is seated on the valve seat 11k and closes the throttling orifice 11d, the rotor 30, valve shaft 21, and valve retainer 23 continue to rotate and descend until they reach the control origin position where the movable stop 35 abuts against the fixed stop 55 and are locked in place. As a result, the coil spring 24 is compressed. Therefore, the needle valve 25 is pressed forcefully against the valve seat 11k by the force of the coil spring 24, reliably preventing refrigerant leakage, etc.

[0091] On the other hand, when the stator is powered by a pulse of opposite polarity from the control origin position, the rotor 30 and valve shaft 21 are driven to rotate in the opposite direction to the valve closing position. Through the threaded feed mechanism consisting of the internal threaded hole 15c and the external threaded portion 21b, the rotor 30, valve shaft 21, valve retainer 23, and movable stop 36 for the valve opening direction rotate and rise simultaneously. Simultaneously, the pressure on the needle valve 25 decreases, the coil spring 24 extends, and the throttling orifice opens when the needle valve 25 leaves the valve seat 11k. Thus, the refrigerant entering the valve chamber 29 from the second pipe T2 flows through the gap between the conical portion 25d and the valve seat 11k, and through the cylindrical hole 11i to the first pipe T1.

[0092] In this case, the lifting amount of the needle valve 25 is determined based on the pulse power supply to the stator, thus enabling refrigerant flow control. Furthermore, through continuous pulse power supply, the needle valve 25 eventually becomes fully open. Moreover, under continuous pulse power supply, the movable stop 36 is locked against the valve opening direction by the fixed stop 56, thereby forcibly stopping the rotation and lifting of the rotor 30, valve shaft 21, and valve holder 23.

[0093] According to this embodiment, when the valve is opened, the refrigerant entering the cylindrical hole 11i of the valve seat component 11 through the gap between the conical portion 25d and the valve seat 11k comes into contact with the bottom wall 11h, changing its flow direction, and flows out of the valve seat component 11 through the cylindrical rectifying hole 11j. At this time, the refrigerant passes through the rectifying hole 11j, thereby exerting a rectification effect, thus miniaturizing the bubbles in the gas-liquid two-phase state and the bubbles generated when passing through the throttling hole, thereby reducing the noise when bubbles burst. In addition, the refrigerant passes through four rectifying holes 11j, so the flow force is dispersed, thereby accelerating the pressure recovery and suppressing the generation of bubbles that cause noise. Furthermore, by giving the valve seat component 11 a rectification effect, a separate rectification component is not required, reducing the number of parts.

[0094] In addition, according to this embodiment, the refrigerant after passing through the cylindrical orifice 11i, which serves as a throttling orifice, flows out by colliding with the inner wall of the first piping T1 through the rectifying orifice 11j. Therefore, the refrigerant flow rate can be forcibly reduced, and the refrigerant pressure can be restored before turbulence occurs. As a result, the generation of bubbles, which is a cause of noise, can be suppressed.

[0095] Furthermore, when the refrigerant flows from the first pipe T1 towards the second pipe T2, the refrigerant entering the valve seat component 11 from the first pipe T1 changes its flow direction through the rectifying orifice 11j, and does not flow directly towards the throttling orifice. Therefore, the faster-flowing refrigerant will not pass through the throttling orifice, which can suppress the vibration of the needle valve 25 when the valve is opened.

[0096] [Second Implementation]

[0097] Figure 5 This is a longitudinal sectional view of the valve seat component 11A, which can be used in the electric valve of the second embodiment. The electric valve structure other than the valve seat component 11A is the same as that of the first embodiment, so repeated descriptions are omitted.

[0098] In this embodiment, the valve seat component 11A is relative to Figure 2 The valve seat component 11 shown differs primarily in that a tapered portion 11Am is formed at the lower end of the cylindrical orifice 11Ai in the bottom wall 11Ah. The rectifier orifice 11Aj contacts a portion of the tapered portion 11Am. The central axis X of the rectifier orifice 11Aj is parallel to the first piping T1 (see reference). Figure 1 The inner walls of the rectifier orifice 11Aj intersect with the axis L at an angle θ greater than 0 degrees and less than 90 degrees. In this embodiment, the lower end of the inner cylindrical portion 11Ae also has a frustum-shaped portion 11Af. For structures common to the first embodiment, the same symbols are used and repeated descriptions are omitted.

[0099] When the valve is opened, the refrigerant, after passing through the throttling orifice, flows along the cylindrical orifice 11Ai, which serves as the throttling orifice, and reaches the conical portion 11Am. At least a portion of the refrigerant enters the rectifying orifice 11Aj after being retained in the conical portion 11Am, thus facilitating the restoration of refrigerant pressure. Furthermore, it also disperses air bubbles as the refrigerant passes through the edge of the conical portion 11Am. Moreover, the conical portion 11Am can be formed by shaping the tip of a cutting tool when forming the cylindrical orifice 11Ai using a cutting tool such as a drill bit.

[0100] [Third Implementation Method]

[0101] Figure 6 This is a longitudinal sectional view of the valve seat component 11B, which can be used in the electric valve of the third embodiment. The electric valve structure other than the valve seat component 11B is the same as that of the first embodiment, so repeated descriptions are omitted.

[0102] In this embodiment, the valve seat component 11B is relative to Figure 2 The valve seat component 11 shown differs primarily in the formation of the connecting opening 11Bm, which extends parallel to the axis L from the center of each rectifier hole 11Bj through the bottom wall 11Bh, and the end of the connecting opening 11Bm is located on the top (lower) surface of the frustum-shaped portion 11f. The inner diameter of the connecting opening 11Bm is preferably less than 1 / 4 of the inner diameter of the rectifier hole Bj. The central axis X of the rectifier hole 11Bj is parallel to the first piping T1 (see reference). Figure 1 The inner walls of the rectifier orifice 11Bj intersect with the axis L at an angle θ greater than 0 degrees and less than 90 degrees. In this embodiment, the lower end of the inner cylindrical portion 11Be also has a frustum-shaped portion 11Bf. For structures common to the first embodiment, the same symbols are used and repeated descriptions are omitted.

[0103] When the valve is opened, the refrigerant, after passing through the throttling orifice, flows along the cylindrical hole 11Bi, which serves as the throttling orifice, and reaches the bottom wall 11Bh. From here, the refrigerant flows out to the outside of the valve seat component 11B through the rectifying hole 11Bj, but at this time it may collide with the inner wall of the first piping T1, forming a vortex. This vortex may hinder the pressure recovery of the refrigerant.

[0104] In contrast, according to this embodiment, a negative pressure is generated inside the connecting opening 11Bm when the refrigerant passes through the upper end of the connecting opening 11Bm, thus drawing the refrigerant up from the lower end of the connecting opening 11Bm. This allows the vortex formed by the collision with the inner wall of the first piping T1 to quickly disappear.

[0105] [Fourth Implementation Method]

[0106] Figure 7This is a longitudinal sectional view of the valve seat component 11C, which can be used in the electric valve of the fourth embodiment. The electric valve structure other than the valve seat component 11C is the same as that of the first embodiment, so repeated descriptions are omitted.

[0107] The valve seat component 11C in this embodiment differs mainly in the shape of the inner cylindrical portion 11Ce and the rectifier orifice 11Cj. For structures common to the first embodiment, the same symbols are used, and repeated descriptions are omitted.

[0108] The inner cylindrical portion 11Ce extending downward from the partition wall portion 11d is composed of an enlarged portion 11Ce1 on the partition wall portion 11d side and a reduced portion 11Ce2 on the top side with an outer diameter smaller than that of the enlarged portion 11Ce1. First piping T1 ( Figure 1 It only fits into the enlarged diameter section 11Ce1.

[0109] Multiple rectifying holes 11Cj are formed to extend obliquely from the lower end of the cylindrical hole 11Ci formed inside the inner cylindrical portion 11Ce toward the valve seat 11k. The rectifying holes 11Cj face the inner wall of the first pipe T1 mounted on the valve seat component 11C. That is, the central axis X of the rectifying holes 11Cj is perpendicular to the first pipe T1 (see reference). Figure 1 The inner walls of the rectifier orifice 11Cj intersect with the axis L at an angle θ greater than 90 degrees and less than 180 degrees.

[0110] In this embodiment, the length of the rectifying orifice 11Cj (the shortest length along the axial direction of the inner wall of the orifice) is longer than the inner diameter of the rectifying orifice 11Cj and longer than the inner circumferential radius of the cylindrical orifice 11Ci. Furthermore, the total flow path cross-sectional area of ​​the four rectifying orifices 11Cj is greater than the throttling cross-sectional area when the valve is fully open. Additionally, the flow path cross-sectional area of ​​the cylindrical orifice 11Ci is greater than or equal to the throttling cross-sectional area when the valve is fully open. Preferably, the total flow path cross-sectional area of ​​the rectifying orifices 11Cj is greater than the flow path cross-sectional area of ​​the cylindrical orifice 11Ci.

[0111] When the valve is opened, the refrigerant flows through the throttling orifice along the cylindrical hole 11Ci, which is the throttling orifice, and reaches the bottom wall 11Ch. Here, the direction of refrigerant flow is bent at an acute angle and flows out to the outside of the valve seat component 11C through the straightening hole 11Cj.

[0112] Because there is a gap between the first pipe T1 and the reduced diameter section 11Ce2, the refrigerant flowing out of the reduced diameter section 11Ce2 comes into contact with the inner wall of the first pipe T1, and then flows downward through the gap between the first pipe T1 and the reduced diameter section 11Ce2. At this time, the flow rate of the refrigerant flowing out from between the first pipe T1 and the reduced diameter section 11Ce2 is slower than the flow rate of the refrigerant passing through the throttling cross-sectional area when the valve is fully open.

[0113] [Fifth Implementation]

[0114] Figure 8 This is a longitudinal sectional view of the valve seat component 11D, which can be used in the electric valve of the fifth embodiment. The electric valve structure other than the valve seat component 11D is the same as that of the first embodiment, so repeated descriptions are omitted.

[0115] The valve seat component 11D in this embodiment differs mainly in the shape of the inner cylindrical portion 11De and the rectifier orifice 11Dj. The same symbols are used for structures common to the first embodiment, and repeated descriptions are omitted.

[0116] 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 top side with an outer diameter smaller than that of the enlarged diameter portion 11De1. First piping T1 ( Figure 1 It only fits into the enlarged diameter section 11De1.

[0117] The rectifying orifice 11Dj is formed to extend from the lower end of the cylindrical hole 11Di formed inside the inner cylindrical portion 11De in a direction orthogonal to the axis L, that is, the rectifying orifice 11Dj intersects the cylindrical hole 11Di, which serves as a throttling orifice, at a right angle. The rectifying orifice 11Dj faces the inner wall of the first pipe T1 mounted on the valve seat component 11D. In other words, the central axis X of the rectifying orifice 11Dj is perpendicular to the first pipe T1 (see reference). Figure 1 The inner walls of the rectifier hole 11Dj intersect at a 90-degree angle θ relative to the axis L.

[0118] In this embodiment, the length of the rectifying orifice 11Dj is preferably longer than its inner diameter and longer than the inner circumferential radius of the cylindrical orifice 11Di. Furthermore, the flow path cross-sectional area of ​​the rectifying orifice 11Dj is greater than the throttling cross-sectional area at maximum valve opening. Additionally, the minimum flow path cross-sectional area of ​​the cylindrical orifice 11Di is greater than or equal to the throttling cross-sectional area at maximum valve opening. The flow path cross-sectional area of ​​the rectifying orifice 11Dj is preferably greater than the flow path cross-sectional area of ​​the cylindrical orifice 11Di.

[0119] When the valve is opened, the refrigerant after passing through the throttling orifice flows along the cylindrical hole 11Di, which is the throttling orifice, and reaches the bottom wall 11Dh. Here, the direction of refrigerant flow is bent at a right angle, and flows out to the outside of the valve seat component 11D through the straightening hole 11Dj.

[0120] Because there is a gap between the first pipe T1 and the reduced-bore section 11De2, the refrigerant flowing out of the reduced-bore section 11De2 comes into contact with the inner wall of the first pipe T1, and then flows downward through the gap between the first pipe T1 and the reduced-bore section 11De2. At this time, the flow rate of the refrigerant flowing out between the first pipe T1 and the reduced-bore section 11De2 is slower than the flow rate of the refrigerant through the throttling cross-sectional area when the valve is fully open.

[0121] [Sixth Implementation Method]

[0122] Figure 9 This is a longitudinal sectional view of the valve seat component 11E, which can be used in the electric valve of the sixth embodiment. The electric valve structure other than the valve seat component 11E is the same as that of the first embodiment, so repeated descriptions are omitted.

[0123] The valve seat component 11E in this embodiment differs mainly in the shape of the cylindrical bore 11Ei. In this embodiment, the central axis X of the rectifier bore 11Ej is also aligned with the first piping T1 (see reference). Figure 1 The inner walls of the rectifier orifice 11Ej intersect with the axis L at an angle θ greater than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ee has a frustum-shaped portion 11Ef. For structures common to the first embodiment, the same symbols are used and repeated descriptions are omitted.

[0124] The cylindrical bore 11Ei has: a first bore 11Ei1 disposed below the valve seat 11k, a second bore 11Ei2 with a diameter larger than the first bore 11Ei1, and a third bore 11Ei3 with a diameter larger than the second bore 11Ei2. The first bore 11Ei1 and the second bore 11Ei2 are connected by a first tapered portion 11Ei4, and the second bore 11Ei2 and the third bore 11Ei3 are connected by a second tapered portion 11Ei5. The lower end of the third bore 11Ei3 (and the second tapered portion 11Ei5) is connected to four rectifying holes 11Ej. Furthermore, the cylindrical bore 11Ei can be formed using, for example, an end mill tool with a shank diameter smaller than the outer diameter of the cutting tip. In addition, the flow path cross-sectional area of ​​the first bore 11Ei1 is greater than or equal to the throttling cross-sectional area when the valve is fully open. The total flow path cross-sectional area of ​​the rectifying holes 11Ej is preferably greater than the flow path cross-sectional area of ​​the first bore 11Ei1.

[0125] When the valve is opened, the refrigerant, after passing through the throttling orifice, flows along the first orifice 11Ei1, the first cone 11Ei4, the second orifice 11Ei2, the second cone 11Ei5, and the third orifice 11Ei3 to reach the bottom wall 11Eh. At this point, the flow path cross-sectional area expands in three stages from the throttling orifice to the bottom wall 11Eh. This allows the refrigerant pressure to gradually recover.

[0126] Furthermore, the refrigerant flows out to the outside of the valve seat component 11E through the downward-facing rectifier orifice 11Ej and contacts the inner wall of the first piping T1, thereby forcibly reducing the refrigerant flow rate and restoring the refrigerant pressure before turbulence occurs.

[0127] [Seventh Implementation Method]

[0128] Figure 10 This is a longitudinal sectional view of the valve seat component 11F, which can be used in the electric valve of the seventh embodiment. The electric valve structure other than the valve seat component 11F is the same as that of the first embodiment, so repeated descriptions are omitted.

[0129] The valve seat component 11F in this embodiment differs mainly in the shape of the cylindrical bore 11Fi. In this embodiment, the central axis X of the rectifying bore 11Fj is also aligned with the first piping T1 (see reference). Figure 1 The inner walls of the rectifier orifice 11Fj intersect with the axis L at an angle θ greater than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Fe has a frustum-shaped portion 11Ff. For structures common to the first embodiment, the same symbols are used and repeated descriptions are omitted.

[0130] The cylindrical bore 11Fi has a first bore 11Fi1 disposed below the valve seat 11k and a second bore 11Fi2 with a diameter larger than the first bore 11Fi1. The first bore 11Fi1 and the second bore 11Fi2 are connected by a tapered portion 11Fi3. The lower end of the second bore 11Fi2 is connected to four rectifying holes 11Fj. Furthermore, the cylindrical bore 11Fi can be formed using, for example, an end mill tool with a shank diameter smaller than the outer diameter of the cutting tip. In addition, the flow path cross-sectional area of ​​the first bore 11Fi1 is greater than or equal to the throttling cross-sectional area when the valve is fully open. The total flow path cross-sectional area of ​​the rectifying holes 11Fj is preferably greater than the flow path cross-sectional area of ​​the first bore 11Fi1.

[0131] When the valve is opened, the refrigerant flows through the throttling orifice along the first orifice 11Fi1, the cone 11Fi3, and the second orifice 11Fi2 to reach the bottom wall 11Fh. At this time, the flow path cross-sectional area expands in two stages from the throttling orifice to the bottom wall 11Fh. As a result, the refrigerant pressure can be gradually restored.

[0132] Furthermore, the refrigerant flows out to the outside of the valve seat component 11F through the downward-facing rectifier orifice 11Fj and contacts the inner wall of the first piping T1, thereby forcibly reducing the refrigerant flow rate and restoring the refrigerant pressure before turbulence occurs.

[0133] [Eighth Implementation Method]

[0134] Figure 11 This is a longitudinal sectional view of the valve seat component 11G, which can be used in the electric valve of the eighth embodiment. The electric valve structure other than the valve seat component 11G is the same as that of the first embodiment, so repeated descriptions are omitted.

[0135] The valve seat component 11G in this embodiment differs mainly in that the central hole 11Gn, which is connected to the cylindrical hole 11Gi, is formed in the bottom wall 11Gh. In this embodiment, the central axis X of the rectifying hole 11Gj is also aligned with the first piping T1 (see reference). Figure 1The inner walls of the rectifier orifice 11Gj intersect with the axis L at an angle θ greater than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ge has a frustum-shaped portion 11Gf. For structures common to the first embodiment, the same symbols are used and repeated descriptions are omitted.

[0136] The central hole 11Gn is coaxial with the cylindrical hole 11Gi and has an inner diameter smaller than that of the cylindrical hole 11Gi and the rectifier hole 11Gj. The ends of the cylindrical hole 11Gi and the rectifier hole 11Gj can be in contact with each other or can be separated from each other.

[0137] When the valve is opened, the refrigerant, after passing through the throttling orifice, flows along the cylindrical orifice 11Gi, which serves as the throttling orifice, and reaches the bottom wall 11Gh. Here, a portion of the refrigerant flows outward from the valve seat component 11G through the rectifying orifice 11Gj and collides with the first piping T1, but eddies may form at this time. On the other hand, although the remaining refrigerant reaching the bottom wall 11Gh flows directly outward from the valve seat component 11G through the central orifice 11Gn, this has the effect of eliminating the eddies formed on the inner wall of the first piping T1. As a result, rapid refrigerant pressure recovery can be achieved.

[0138] [Ninth Implementation Method]

[0139] Figure 12 This is a longitudinal sectional view of the valve seat component 11H, which can be used in the electric valve of the ninth embodiment. The electric valve structure other than the valve seat component 11H is the same as that of the first embodiment, so repeated descriptions are omitted.

[0140] Reference Figure 12 The cross-section obtained by cutting the electric valve 1 with a plane passing through axis L and central axis X (here, Figure 12 In the diagram, the inner wall of the rectifier orifice 11Hj is represented as a pair of line segments separated by a central axis X, the central axis X of the rectifier orifice 11Hj being connected to the straight line connecting one end of each line segment of the inner wall. Figure 12 (The dashed line) PL1 and the straight line connecting the other ends to each other ( Figure 12 When the dashed line PL2 intersects at points PT1 and PT2, the distance between these points PT1 and PT2 is the length of the rectifier orifice 11Hj. In this embodiment, the central axis X of the rectifier orifice 11Hj is also intersected by the first pipe T1 (refer to...). Figure 1 The inner walls of the rectifier orifice 11Hj intersect with the axis L at an angle θ greater than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical part 11He has a frustum-shaped part 11Hf.

[0141] The valve seat component 11H in this embodiment differs mainly in the shape of the cylindrical bore 11Hi and the formation of the central hole 11Hn connected to the cylindrical bore 11Hi in the bottom wall 11Hh. For structures common to the first embodiment, the same symbols are used and repeated descriptions are omitted.

[0142] The cylindrical bore 11Hi has a first bore 11Hi1 disposed below the valve seat 11k and a second bore 11Hi2 with a diameter larger than the first bore 11Hi1. The first bore 11Hi1 and the second bore 11Hi2 are connected by a tapered portion 11Hi3. The lower end of the second bore 11Hi2 is connected to four flow-rectifying holes 11Hj. Furthermore, the cylindrical bore 11Hi can be formed using, for example, an end mill tool with a shank diameter smaller than the tip diameter. In addition, the flow path cross-sectional area of ​​the first bore 11Hi1 is greater than or equal to the throttling cross-sectional area when the valve is fully open. The total flow path cross-sectional area of ​​the flow-rectifying holes 11Hj is preferably greater than the flow path cross-sectional area of ​​the first bore 11Hi1.

[0143] The central hole 11Hn is coaxial with the cylindrical hole 11Hi and has an inner diameter smaller than that of the cylindrical hole 11Hi and the rectifier hole 11Hj.

[0144] When the valve is opened, the refrigerant, after passing through the throttling orifice, flows along the first orifice 11Hi1, the cone 11Hi3, and the second orifice 11Hi2 to reach the bottom wall 11Hh. At this point, the flow path cross-sectional area expands in two stages from the throttling orifice to the bottom wall 11Hh. This allows the refrigerant pressure to gradually recover.

[0145] A portion of the refrigerant reaching the bottom wall 11Hh flows out through the rectifier hole 11Hj to the outside of the valve seat component 11H and collides with the first piping T1, potentially forming eddies. On the other hand, while the remaining refrigerant reaching the bottom wall 11Hh flows directly through the central hole 11Hn to the outside of the valve seat component 11H, this effectively eliminates the eddies formed on the inner wall of the first piping T1. Therefore, rapid refrigerant pressure recovery is possible.

[0146] [Tenth Implementation Method]

[0147] Figure 13 This is a longitudinal sectional view of the valve seat component 11I, which can be used in the electric valve of the tenth embodiment. The electric valve structure other than the valve seat component 11I is the same as that of the first embodiment, so repeated descriptions are omitted.

[0148] The main difference in the valve seat component 11I of this embodiment lies in the positional relationship between the cylindrical bore 11Ii and the rectifier bore 11Ij. In this embodiment, the central axis X of the rectifier bore 11Ij is also aligned with the first piping T1 (see reference). Figure 1The inner walls of the rectifier orifice 11Ij intersect with the axis L at an angle θ greater than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ie has a frustum-shaped portion 11If. For structures common to the first embodiment, the same symbols are used and repeated descriptions are omitted.

[0149] In this embodiment, the rectifier hole 11Ij is connected between the lower end and the upper end of the cylindrical hole 11Ii. As a result, a refrigerant retention portion 11Ip is formed on the bottom wall 11Ih from the lower end of the cylindrical hole 11Ii to the connection portion connected to the rectifier hole 11Ij.

[0150] When the valve is opened, the refrigerant, after passing through the throttling orifice, flows along the cylindrical hole 11Ii, which serves as the throttling orifice, and reaches the stagnation section 11Ip on the bottom wall 11Ih. Here, the refrigerant flow makes a U-turn and flows out to the outside of the valve seat component 11I through the rectifier hole 11Ij. At this time, the refrigerant pressure is restored, which can reduce the number of bubbles.

[0151] [Eleventh Implementation Method]

[0152] Figure 14 This is a longitudinal sectional view of the valve seat component 11K, which can be used in the electric valve of the eleventh embodiment. The electric valve structure other than the valve seat component 11K is the same as that of the first embodiment, so repeated descriptions are omitted.

[0153] The valve seat component 11K in this embodiment differs mainly in structure from the inner cylindrical portion 11Ke. In this embodiment, the central axis X of the rectifier orifice 11Kj is also aligned with the first piping T1 (see reference). Figure 1 The inner walls of the rectifier orifice 11Kj intersect with the axis L at an angle θ greater than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ke has a frustum-shaped portion 11Kf. For structures common to the first embodiment, the same symbols are used and repeated descriptions are omitted.

[0154] The inner cylindrical portion 11Ke extending downward from the partition wall portion 11d is composed of an expanding portion 11Ke1 on the partition wall portion 11d side and a narrowing portion 11Ke2 on the top side with an outer diameter smaller than that of the expanding portion 11Ke1. A frustoconical portion 11Kf is formed at the lower end of the narrowing portion 11Ke2. First piping T1 ( Figure 1 It only fits into the enlarged diameter section 11Ke1.

[0155] Multiple rectifier holes 11Kj are formed to extend downward at an angle from the lower end of the cylindrical hole 11Ki formed inside the inner cylindrical portion 11Ke toward the valve seat 11k side. Additionally, a connecting opening 11Kn is formed extending at an angle from the middle position of each rectifier hole 11Kj toward the partition wall portion 11d side. The inner diameter of the connecting opening 11Kn is preferably less than 1 / 4 of the inner diameter of the rectifier hole Kj.

[0156] When the valve is opened, the refrigerant, after passing through the throttling orifice, flows along the cylindrical hole 11Ki, which serves as the throttling orifice, and reaches the bottom wall 11Kh. From here, the refrigerant flows out to the outside of the valve seat component 11K through the rectifying orifice 11Kj, but at this time it may collide with the inner wall of the first piping T1, forming a vortex. This vortex may hinder the pressure recovery of the refrigerant.

[0157] In contrast, according to this embodiment, when the refrigerant passes through the lower end of the connecting opening 11Kn, a negative pressure is generated inside the connecting opening 11Kn, thus drawing in refrigerant from the upper end of the connecting opening 11Kn. This allows the vortex formed by the collision with the inner wall of the first pipe T1 to quickly disappear.

[0158] [Variation Example]

[0159] Figure 15 This diagram shows the structure of the electric valve seat component 11 and the porous filter FT combined in a modified example of this embodiment. The left half is a longitudinal sectional view, and the right half is a side view. The structure other than the porous filter FT is the same as in the first embodiment, therefore repeated descriptions are omitted.

[0160] A porous filter FT, made of metal or resin, is disposed around the inner cylindrical portion 11e of the valve seat component 11, extending from the position shown by the dotted line to the bottom of the frustum-shaped portion 11f. The porous filter FT is formed into a cylindrical shape by means of, for example, foamed metal, mesh material, or stamped metal, and is wound around the outer periphery of the inner cylindrical portion 11e to cover the outer end of the flow-rectifying orifice 11j.

[0161] The refrigerant flowing out of the rectifier orifice 11j passes through the porous filter FT, thus breaking down the bubbles and further reducing noise. The valve seat component combined with the porous filter FT is not limited to the first embodiment, but can also be combined with embodiments other than the first embodiment.

[0162] In the above embodiments, when the cross angle θ is less than 90 degrees, the cross angle θ is preferably 15 degrees or more and 75 degrees or less, more preferably 30 degrees or more and 60 degrees or less. In addition, when the cross angle θ exceeds 90 degrees, the cross angle θ is preferably 105 degrees or more and 165 degrees or less, more preferably 120 degrees or more and 150 degrees or less.

Claims

1. An electric valve, characterized in that, have: Valve body, which includes a valve chamber; A valve seat assembly, which is mounted on the valve body and has a valve seat; and A valve core, which is disposed in the valve chamber and is capable of moving up and down in the direction of approaching or moving away from the valve seat. The valve seat component is connectable to a piping system and includes a throttling orifice, a rectifying orifice, and a bottom wall. The throttling orifice is adjacent to the valve seat, the rectifying orifice is connected to the throttling orifice, and the bottom wall is formed at the end of the throttling orifice. In a cross-section obtained by cutting the electric valve with a plane passing through the axis of the electric valve and the central axis of the rectifier orifice, the intersection point of the axis of the electric valve and the central axis of the rectifier orifice is located on the side closer to the bottom wall compared to the valve seat. The central axis of the rectifier orifice intersects the inner wall of the piping. The valve seat component includes a cylindrical portion, inside which the throttling orifice portion is formed, and the cylindrical portion is disposed within the piping. The electric valve has a communication opening that extends from the rectifier orifice to the outside of the valve seat component, the inner diameter of the communication opening being smaller than the inner diameter of the rectifier orifice.

2. The electric valve according to claim 1, characterized in that, The rectifying orifice branches into multiple parts from the throttling orifice.

3. The electric valve according to claim 1 or 2, characterized in that, The total flow path cross-sectional area of ​​the rectifier orifice is greater than the throttling cross-sectional area when the valve is fully open.

4. The electric valve according to claim 3, characterized in that, The flow path cross-sectional area of ​​the throttling orifice is greater than or equal to the throttling cross-sectional area when the valve is at its maximum opening.

5. The electric valve according to claim 3, characterized in that, The total flow path cross-sectional area of ​​the rectifying orifices is greater than the flow path cross-sectional area of ​​the throttling orifice.

6. The electric valve according to claim 1 or 2, characterized in that, The length of the rectifier orifice is longer than the inner diameter of the rectifier orifice, and also longer than the inner circumferential radius of the throttling orifice.

7. The electric valve according to claim 1 or 2, characterized in that, A frustum-shaped portion is formed at the end of the cylindrical portion, and the outer end of the rectifier hole is located on the outer circumferential surface of the frustum-shaped portion.

8. The electric valve according to claim 1 or 2, characterized in that, A tapered portion is formed at the inner end of the throttling orifice.

9. The electric valve according to claim 1 or 2, characterized in that, The rectifier orifice intersects with the throttling orifice.

10. The electric valve according to claim 1 or 2, characterized in that, The rectifier orifice intersects the throttling orifice at a right angle.

11. The electric valve according to claim 1 or 2, characterized in that, The throttling orifice has a first hole and a second hole with a diameter larger than the first hole, starting from the valve seat side.

12. The electric valve according to claim 1 or 2, characterized in that, The throttling orifice has, in sequence from the valve seat side, a first orifice, a second orifice with a diameter larger than the first orifice, and a third orifice with a diameter larger than the second orifice.

13. The electric valve according to claim 1 or 2, characterized in that, It has a central hole connected to the throttling orifice and extending in the same direction as the throttling orifice, the inner diameter of the central hole being smaller than the inner diameter of the rectifying orifice.

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