JP7374522B2 - electric valve - Google Patents

Description

The present invention relates to a motor-operated valve such as a flow rate adjustment valve used to adjust the flow rate of refrigerant in, for example, a heat pump type air conditioning system.

A flow rate regulating valve that is an example of a conventional electric valve is disclosed in Patent Document 1. The flow rate regulating valve of Patent Document 1 has a valve chamber and a valve port provided in the valve body. The diameter of the valve port is gradually increased in three or more steps as the distance from the valve chamber increases. This reduces the noise generated when the refrigerant passes through the valve port.

JP2017-89864A

However, depending on the system in which the electric valve is used, further noise reduction is required.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide an electric valve that can effectively reduce the noise generated when refrigerant flows through a valve port.

In order to achieve the above object, an electrically operated valve according to one aspect of the present invention includes a valve body provided with a valve chamber and a valve port, and a valve body disposed to face the valve port. The valve port is an electrically operated valve, and the valve port includes a first circumferential surface and a first tapered surface that is disposed further from the valve chamber than the first circumferential surface and whose diameter increases as the distance from the valve chamber increases. a second circumferential surface that is disposed further from the valve chamber than the first tapered surface and has a larger diameter than the first circumferential surface; and a second circumferential surface that is disposed further from the valve chamber than the second circumferential surface and that and a second tapered surface that is arranged farther from the valve chamber than the annular plane and has a diameter that increases as it moves away from the valve chamber.

In the present invention, it is preferable that the length of the second circumferential surface in the axial direction is longer than the length of the first circumferential surface in the axial direction.

In the present invention, when the axial length of the first circumferential surface is L1 and the axial length of the second circumferential surface is L2, it is preferable that the following formula (1) is satisfied.
2≦L2/L1≦133.3... (1)

In the present invention, when the diameter of the first circumferential surface is D1, it is preferable that the following formula (2) is satisfied.
0.4≦L2/D1≦25... (2)

In the present invention, it is preferable that the following formula (3) be satisfied, where the diameter of the first circumferential surface is D1 and the diameter of the second circumferential surface is D2.
1.01≦D2/D1≦1.55 (3)

In the present invention, when the taper angle of the first tapered surface is θ1 and the taper angle of the second tapered surface is θ2, it is preferable that the following equations (4) and (5) are satisfied.
60 degrees≦θ1≦120 degrees... (4)
40 degrees≦θ2≦150 degrees... (5)

In the present invention, the second circumferential surface may have a plurality of circumferential surface portions whose diameter gradually increases as the distance from the valve chamber side increases.

The motor-operated valve includes a valve body provided with a valve chamber and a valve port, and a valve body disposed in the valve chamber so as to face the valve port, and the valve port includes: a first circumferential surface connected in order in the axial direction from the valve chamber side; and a first tapered surface whose diameter increases as the distance from the valve chamber increases; a second circumferential surface that is connected in order to the valve chamber and is located further away from the valve chamber than the first tapered surface and has a larger diameter than the first circumferential surface; an annular plane perpendicular to the axial direction; It is characterized by having a second tapered surface whose diameter increases as the distance increases.

In the present invention, the first tapered surface and the second circumferential surface may be connected.

In the present invention, (a) one intermediate circumferential surface having a diameter larger than the first circumferential surface and smaller than the second circumferential surface is disposed between the first tapered surface and the second circumferential surface. or (b) a plurality of intermediate circumferential surfaces are arranged, each having a larger diameter than the first circumferential surface and a smaller diameter than the second circumferential surface, the diameter of which gradually increases as the distance from the valve chamber increases. may have been done.

In the present invention, when the length of the first circumferential surface in the axial direction is L1, and the length between the first tapered surface and the annular plane is L2, the following formula (1) can be satisfied. preferable.
2≦L2/L1≦133.3... (1)

In the present invention, when the diameter of the first circumferential surface is D1, it is preferable that the following formula (2) is satisfied.
0.4≦L2/D1≦25... (2)

The present invention may include a cylindrical can attached to the valve body, a magnetic rotor housed in the can, and a cylindrical stator into which the can is fitted.

According to the present invention, noise generated when refrigerant flows through a valve port can be effectively reduced.

1 is a sectional view showing the configuration of a flow rate regulating valve according to a first embodiment of the present invention. FIG. 2 is an enlarged sectional view showing the valve seat member of the flow rate regulating valve of FIG. 1 and its vicinity. FIG. 2 is a sectional view of a valve seat member of the flow rate regulating valve of FIG. 1. FIG. FIG. 4 is a sectional view showing the structure of a modification of the valve seat member of FIG. 3; FIG. 4 is a sectional view showing the configuration of another modification of the valve seat member of FIG. 3; It is a sectional view showing the composition of the flow rate adjustment valve concerning a 2nd embodiment of the present invention. FIG. 7 is an enlarged sectional view showing the valve seat member of the flow rate regulating valve of FIG. 6 and its vicinity. FIG. 7 is a sectional view of the valve seat member of the flow rate regulating valve of FIG. 6; FIG. 9 is a sectional view showing a configuration of a modified example of the valve seat member of FIG. 8; 9 is a sectional view showing the configuration of another modification of the valve seat member of FIG. 8. FIG. It is a graph showing the relationship between the ratio D2/D1 and the evaluation value E. It is a graph showing the relationship between the taper angle θ1 of the first tapered surface and the evaluation value E. It is a graph showing the relationship between the taper angle θ2 of the second tapered surface and the evaluation value E. It is a graph showing the relationship between the length L2 of the second circumferential surface and the evaluation value E. It is a graph showing the relationship between the length L1 of the first circumferential surface and the evaluation value E.

(First embodiment)
A flow rate regulating valve according to a first embodiment of the present invention will be described below with reference to FIGS. 1 to 5.

FIG. 1 is a cross-sectional view (a cross-sectional view along the axis) showing the configuration of a flow rate regulating valve according to a first embodiment of the present invention. FIG. 2 is an enlarged sectional view showing the valve seat member of the flow rate regulating valve of FIG. 1 and its vicinity. In FIGS. 1 and 2, the valve body and the coupling mechanism are shown in shapes viewed from the front, not in cross section. FIG. 3 is a sectional view of the valve seat member of the flow rate regulating valve of FIG. 1. FIG. 4 is a cross-sectional view showing the configuration of a first modified example of the valve seat member shown in FIG. 3. FIG. FIG. 5 is a sectional view showing the configuration of a second modified example of the valve seat member of FIG. 3. FIG. In addition, in the following description, "up and down" indicates the positional relationship in each figure, and does not indicate the absolute positional relationship of each component.

The flow rate adjustment valve 1 of this embodiment is, for example, an electric valve used to adjust the flow rate of a refrigerant as a fluid in a heat pump air conditioning system or the like.

As shown in FIGS. 1 to 3, the flow rate adjustment valve 1 includes a valve body 10, a valve body 40, a can 50, a guide stem 60, a valve shaft 70, a coupling mechanism 78, a magnetic rotor 80, It has a stator 90.

The valve body 10 includes a valve seat member 11 and a case member 18.

The valve seat member 11 is manufactured, for example, by cutting a metal material such as stainless steel. The valve seat member 11 includes a bottom wall portion 12 formed in a disk shape, a cylindrical peripheral wall portion 13 extending upward from the upper surface 12a of the bottom wall portion 12, and a cylindrical peripheral wall portion 13 extending downward from the lower surface 12b of the bottom wall portion 12. It has an integral part 14.

The valve seat member 11 is joined to the case member 18 by brazing, with the peripheral wall portion 13 inserted into the lower end of the cylindrical case member 18 . The valve seat member 11 and the case member 18 form a valve chamber 15. A first conduit 6 that passes through the case member 18 in a direction perpendicular to the axis L and is connected to the valve chamber 15 is joined to the case member 18 . Note that the peripheral wall portion 13 has the effect of reducing noise by rectifying the flow of refrigerant flowing from the first conduit 6 into a valve port 30, which will be described later, along the axial direction.

A valve seat 16 is provided on the upper surface 12a of the bottom wall portion 12. The valve seat 16 is a conical tapered surface that faces radially inward and whose diameter decreases as it moves away from the valve chamber 15 .

A circular annular groove 17 is provided on the lower surface 12b of the bottom wall portion 12 so as to surround the cylindrical portion 14. The inner peripheral surface of the annular groove 17 becomes the outer peripheral surface of the cylindrical portion 14 . By inserting the upper end of the second conduit 7 into the annular groove 17, the cylindrical portion 14 is inserted into the upper end of the second conduit 7. Then, the bottom wall portion 12 and the second conduit 7 are joined by brazing.

A valve port 30 serving as a refrigerant flow path is provided so as to penetrate the bottom wall portion 12 and the cylindrical portion 14 . The valve port 30 is a space with a circular cross section that extends linearly. The opening of the valve port 30 on the valve chamber 15 side is surrounded by the valve seat 16. The axis of the valve port 30 coincides with the axis L.

The valve port 30 includes a first circumferential surface 31, a first tapered surface 32, a second circumferential surface 33, an annular plane 34, and a second tapered surface 35, which are connected in order from the valve chamber 15 side in the axis L direction. It has .

The first circumferential surface 31 is a cylindrical circumferential surface facing radially inward. As an example, the diameter D1 of the first peripheral surface 31 is 1.6 mm, and the length L1 in the direction of the axis L is 0.3 mm. The first circumferential surface 31 is connected to the lower end of the valve seat 16.

The first tapered surface 32 is a conical tapered surface that faces radially inward and whose diameter increases as it moves away from the valve chamber 15 . As an example, the taper angle θ1 of the first tapered surface 32 is 80 degrees. The taper angle is also called the apex angle, and is the angle formed by two generatrix lines of a cone in one axial cross section.

The second circumferential surface 33 is a cylindrical circumferential surface facing radially inward. The diameter D2 of the second circumferential surface 33 is larger than the diameter D1 of the first circumferential surface 31. Further, a length L2 of the second circumferential surface 33 in the axis L direction is longer than a length L1 of the first circumferential surface 31 in the axis L direction. As an example, the diameter D2 of the second circumferential surface 33 is 1.9 mm, and the length L2 is 4.6 mm.

The annular plane 34 is a circular annular plane perpendicular to the axis L direction. The inner diameter of the annular plane 34 is equal to the diameter D2 of the second peripheral surface 33. The outer diameter D3 of the annular plane 34 is larger than the diameter D2 of the second peripheral surface 33. As an example, the outer diameter D3 of the annular plane is 4.0 mm.

The second tapered surface 35 is a conical tapered surface that faces radially inward and whose diameter increases as it moves away from the valve chamber 15 . As an example, the taper angle θ2 of the second tapered surface 35 is 60 degrees, and the length L3 of the second tapered surface 35 in the direction of the axis L is 0.9 mm. In this embodiment, the lower end of the second tapered surface 35 becomes the lower end of the cylindrical portion 14 .

Note that the valve port 30 can be rephrased as follows. That is, the valve port 30 has a first circumferential surface 31 and a first tapered surface 32 connected in order in the direction of the axis L from the valve chamber 15 side, and a first circumferential surface 31 and a first tapered surface 32 connected in the direction of the axis L from the valve chamber 15 side. It has a second circumferential surface 33, an annular plane 34, and a second tapered surface 35, which are connected in this order. The first tapered surface 32 and the second circumferential surface 33 are connected.

The valve port 30 satisfies the following equations (1) to (6).
2≦L2/L1≦133.3... (1)
0.4≦L2/D1≦25... (2)
1.01≦D2/D1≦1.55 (3)
60 degrees≦θ1≦120 degrees... (4)
40 degrees≦θ2≦150 degrees... (5)
0.2mm<L1<0.8mm... (6)

The flow rate regulating valve according to the present invention preferably satisfies all of the above formulas (1) to (6), but satisfies one or more of the above formulas (1) to (6). It may be something.

The valve body 40 is formed into a cylindrical shape as a whole. The valve body 40 has a body portion 41, a seating portion 42, and a tip portion 43 that are connected in order in the direction of the axis L from above to below.

The body portion 41 is formed into a cylindrical shape. The outer circumferential surface of the seating portion 42 is a conical tapered surface that faces outward in the radial direction and becomes smaller in diameter toward the valve port 30 (downward). In this embodiment, the tip portion 43 has a shape to obtain a flow rate characteristic that approximates an equal percentage characteristic. The tip portion 43 has a plurality of stages (here, five stages) of conical tapered surface parts 43A to 43E (numerals 43B, 43C, and 43D are not shown). The taper angles of the tapered surface portions 43A to 43E are gradually increased toward the tip so as to simulate an ellipsoidal surface. In this specification, the angle of half the taper angle of the tapered surface portions 43A to 43E (that is, the intersection angle between the generatrix of the tapered surface portion and a line parallel to the axis of the valve body 40 (however, the intersection angle is an inferior angle)) is defined as the inclination angle. That's what it means. This angle of inclination is also called the cone generating angle. The inclination angle θa of the uppermost tapered surface portion 43A closest to the seating portion 42 is normally set to 3°<θa<15° (here, 5°). The lowermost tapered surface portion 43E, which is farthest from the seating portion 42, is a conical surface with a pointed tip. Note that the tip portion 43 may adopt a shape to obtain linear characteristics as the flow rate characteristics.

The valve body 40 is arranged in the valve chamber 15 so that the tip portion 43 faces the valve port 30 in the direction of the axis L and the axis of the valve body 40 coincides with the axis L. The valve body 40 is moved in the direction of the axis L so as to move forward and backward relative to the valve seat 16. The seating portion 42 closes the valve port 30 when it comes into contact with the valve seat 16. The valve body 40 changes the flow rate of the refrigerant flowing through the valve port 30 depending on the distance (lift amount) from the valve seat 16.

The can 50 is formed into a cylindrical shape with a closed upper end. The lower end of the can 50 is fixed to the upper end of the case member 18 of the valve body 10 by welding or the like.

The guide stem 60 includes a cylindrical guide portion 61 and a valve shaft support portion 62 connected to the upper end of the guide portion 61 and provided with a female thread portion 65 . The guide portion 61 is fixed to the upper end of the case member 18 via a flange-like disk 63 by welding or the like. The guide stem 60 is arranged so as to straddle the inside of the case member 18 and the inside of the can 50.

The valve shaft 70 is formed into a cylindrical shape. A male threaded portion 75 is provided on the outer circumferential surface of the valve shaft 70 and is screwed into the female threaded portion 65 of the guide stem 60 . The lower end of the valve shaft 70 is connected to the valve body 40 via a cylindrical connection mechanism 78. The coupling mechanism 78 is disposed inside the guide portion 61 so as to be slidable in the direction of the axis L.

The magnet rotor 80 integrally includes a cylindrical peripheral wall part 81 having an outer diameter slightly smaller than the inner diameter of the can 50, and a ceiling part 82 that closes the upper end of the peripheral wall part 81. The magnet rotor 80 is rotatably housed inside the can. The upper end portion 71 of the valve shaft 70 is attached to the ceiling portion 82 . The valve shaft 70 rotates together with the magnetic rotor 80.

Stator 90 is formed into a substantially cylindrical shape. The can 50 is fitted inside the stator 90. Stator 90 produces a magnetic field that rotates magnet rotor 80 in one direction and the other. The stator 90 and the magnet rotor 80 constitute a stepping motor.

The flow rate regulating valve 1 includes a valve seat member 11 (bottom wall portion 12, peripheral wall portion 13, cylindrical portion 14, valve seat 16, annular groove 17), a case member 18, a valve port 30, a valve body 40, a can 50, and a guide stem. 60, the valve shaft 70, the magnet rotor 80, and the stator 90 have their respective central axes aligned with the axis L. The normal direction of the annular plane 34 of the valve port 30 coincides with the axis L direction.

In the flow rate regulating valve 1, when the stator 90 is energized so that the magnet rotor 80 rotates in one direction, the valve shaft 70 rotates together with the magnet rotor 80. Due to the screw feeding action between the female threaded portion 65 of the guide stem 60 and the male threaded portion 75 of the valve stem 70, the valve stem 70 and the magnet rotor 80 move downward, and the valve body 40 contacts the valve seat 16 (valve closed state). .

Alternatively, in the flow rate regulating valve 1, when the stator 90 is energized so that the magnetic rotor 80 rotates in the other direction, the valve shaft 70 rotates together with the magnetic rotor 80. Due to the thread feeding action between the female threaded portion 65 of the guide stem 60 and the male threaded portion 75 of the valve stem 70, the valve stem 70 and the magnet rotor 80 move upward, and the valve body 40 separates from the valve seat 16 (valve open state). .

As described above, according to the flow rate regulating valve 1 of the present embodiment, the valve port 30 provided in the valve seat member 11 separates from the first circumferential surface 31 and the valve chamber 15, which are connected in order from the valve chamber 15 side. a first tapered surface 32 whose diameter increases as it moves away from the valve chamber 15; a second circumferential surface 33 that has a larger diameter than the first circumferential surface 31; and an annular plane 34 that is perpendicular to the direction of the axis L; The second tapered surface 35 has a second tapered surface 35. By doing so, the noise generated when the refrigerant flows through the valve port 30 can be effectively reduced.

In the configuration in which the second tapered surface 35 is connected to the end of the second circumferential surface 33 via the annular plane 34, the portion of the valve port 30 beyond the end of the second circumferential surface 33 is connected to the annular plane 34 and the second taper surface 35. The diameter is enlarged with respect to the second circumferential surface 33 by the surface 35 . This configuration is called the former configuration. On the other hand, in a configuration in which the second tapered surface 35 is directly connected to the end of the second circumferential surface 33, the portion of the valve port 30 beyond the end of the second circumferential surface 33 is connected only by the second tapered surface 35. The diameter is enlarged relative to the second circumferential surface 33. This configuration is called the latter configuration. Therefore, when the former configuration and the latter configuration are expanded to the same size with the same taper angle θ2, the length of the second tapered surface 35 in the axis L direction can be made shorter in the former configuration than in the latter configuration. In the former configuration, since the length of the second tapered surface 35 in the direction of the axis L is short, the length of the second circumferential surface 33 in the direction of the axis L can be increased. Therefore, the flow rate regulating valve 1 of this embodiment having the former configuration can reduce the flow velocity of the refrigerant at the second circumferential surface 33 no matter which direction the refrigerant flows at the valve port 30, effectively reducing noise. can be reduced to

Furthermore, when the refrigerant flows from the second conduit 7 to the first conduit 6, air bubbles in the refrigerant are crushed and made finer at the corner between the second circumferential surface 33 and the annular plane 34, which effectively reduces noise. Can be reduced. At this time, the second tapered surface 35 creates a flow from the outside in the radial direction to the inside, collects the air bubbles in the refrigerant, increases the speed at which the refrigerant passes through the corner, and promotes the miniaturization of the air bubbles. ing.

In the embodiment described above, the second peripheral surface 33 of the valve seat member 11 has the same diameter D2 throughout the axis L direction, but the present invention is not limited to this configuration. In place of the valve seat member 11, for example, a valve seat member 11A (FIG. 4) of the first modification having a second circumferential surface 33A having a plurality of circumferential surface portions, or a second circumferential surface having a plurality of circumferential surface portions. A configuration may be adopted in which a second modified valve seat member 11B (FIG. 5) having a surface 33B is adopted. In FIGS. 4 and 5, the same components as the valve seat member 11 described above are denoted by the same reference numerals, and the description thereof will be omitted. A modification of the first embodiment will be described below.

(First modification of the first embodiment)
In the valve seat member 11A shown in FIG. 4, a valve port 30A, which is a refrigerant flow path, is provided so as to penetrate the bottom wall portion 12 and the cylindrical portion 14. The valve port 30A has a first circumferential surface 31, a first tapered surface 32, a second circumferential surface 33A, an annular plane 34, and a second tapered surface 35, which are connected in this order from the valve chamber 15 side. are doing.

The second circumferential surface 33A includes a first circumferential surface portion 33A1, an intermediate tapered surface 33A2, and a second circumferential surface portion 33A3, which are connected in order from the valve chamber 15 side in the axis L direction.

The first circumferential surface portion 33A1 is a cylindrical circumferential surface facing radially inward. The diameter D21 of the first circumferential surface portion 33A1 is larger than the diameter D1 of the first circumferential surface 31. The first circumferential surface portion 33A1 is connected to the lower end of the first tapered surface 32. The intermediate tapered surface 33A2 is a conical tapered surface that faces radially inward and whose diameter increases as it moves away from the valve chamber 15. The second circumferential surface portion 33A3 is a cylindrical circumferential surface facing radially inward. The diameter D22 of the second circumferential surface portion 33A3 is larger than the diameter D21 of the first circumferential surface portion 33A1. The second peripheral surface portion 33A3 is connected to the annular plane 34. The length L2 of the second circumferential surface 33A in the axis L direction (that is, the length L21 of the first circumferential surface portion 33A1 in the axis L direction, the length L22 of the intermediate tapered surface 33A2 in the axis L direction, and the second circumferential surface portion 33A3 The total length L23 of the first circumferential surface 31 in the axis L direction is longer than the length L1 of the first circumferential surface 31 in the axis L direction. Further, a length L21 of the first circumferential surface portion 33A1 in the axis L direction is longer than a length L23 of the second circumferential surface portion 33A3 in the axis L direction.

(Second modification of the first embodiment)
The valve seat member 11B shown in FIG. 5 is provided with a valve port 30B, which is a refrigerant flow path, so as to penetrate the bottom wall portion 12 and the cylindrical portion 14. The valve port 30B has a first circumferential surface 31, a first tapered surface 32, a second circumferential surface 33B, an annular plane 34, and a second tapered surface 35, which are connected in order from the valve chamber 15 side. are doing.

The second circumferential surface 33B includes a first circumferential surface portion 33B1, an intermediate tapered surface 33B2, and a second circumferential surface portion 33B3, which are connected in order from the valve chamber 15 side in the axis L direction.

The first circumferential surface portion 33B1 is a cylindrical circumferential surface facing radially inward. The diameter D21 of the first circumferential surface portion 33B1 is larger than the diameter D1 of the first circumferential surface 31. The first circumferential surface portion 33B1 is connected to the lower end of the first tapered surface 32. The intermediate tapered surface 33B2 is a conical tapered surface that faces radially inward and whose diameter increases as it moves away from the valve chamber 15. The second circumferential surface portion 33B3 is a cylindrical circumferential surface facing radially inward. The diameter D22 of the second circumferential surface portion 33B3 is larger than the diameter D21 of the first circumferential surface portion 33B1. The second peripheral surface portion 33B3 is connected to the annular plane 34. The length L2 of the second circumferential surface 33B in the axis L direction (that is, the length L21 of the first circumferential surface portion 33B1 in the axis L direction, the length L22 of the intermediate tapered surface 33B2 in the axis L direction, and the second circumferential surface portion 33B3 The total length L23 of the first circumferential surface 31 in the axis L direction is longer than the length L1 of the first circumferential surface 31 in the axis L direction. Further, the length L21 of the first circumferential surface portion 33B1 in the axis L direction and the length L23 of the second circumferential surface portion 33B3 in the axis L direction are substantially the same.

In each modification of the first embodiment, the length L2 is also the length between the first tapered surface 32 and the annular plane 34. It is preferable that the valve ports 30A and 30B also satisfy one or more of the above equations (1) to (6). Each modification also has the same effects as the flow rate regulating valve 1 of the first embodiment described above.

The second circumferential surface 33A of the first modified example and the second circumferential surface 33B of the second modified example have three or more peripheral surface portions whose diameters gradually increase as they move away from the valve chamber 15. It's okay.

The valve port 30A of the first modification can be rephrased as follows. That is, the valve port 30A has a first circumferential surface 31 and a first tapered surface 32 connected in order from the valve chamber 15 side in the axis L direction, and has a first circumferential surface 31 and a first tapered surface 32 connected in the axis L direction from the valve chamber 15 side. It has a second circumferential surface portion 33A3 (second circumferential surface), an annular plane 34, and a second tapered surface 35, which are connected in this order. A first circumferential surface portion 33A1 (one intermediate circumferential surface) is arranged between the first tapered surface 32 and the second circumferential surface portion 33A3 (instead of one intermediate circumferential surface, the valve A plurality of intermediate circumferential surfaces may be arranged whose diameter increases stepwise as the distance from the chamber 15 increases.The intermediate circumferential surface has a larger diameter than the first circumferential surface 31 and a smaller diameter than the second circumferential surface portion 33A3. be.). The first tapered surface 32 and the second circumferential surface portion 33A3 are connected via the first circumferential surface portion 33A1 and the intermediate tapered surface 33A2. Regarding the valve port 30B of the second modification, the same can be said in other words.

(Second embodiment)
A flow rate regulating valve according to a second embodiment of the present invention will be described below with reference to FIGS. 6 to 10.

FIG. 6 is a cross-sectional view (a cross-sectional view along the axis) showing the configuration of a flow rate regulating valve according to a second embodiment of the present invention. FIG. 7 is an enlarged sectional view showing the valve seat member of the flow rate regulating valve of FIG. 6 and its vicinity. In FIGS. 6 and 7, the valve body and the connection mechanism are shown in shapes viewed from the front, not in cross section. FIG. 8 is a sectional view of the valve seat member of the flow rate regulating valve of FIG. 6. FIG. 9 is a sectional view showing the configuration of a first modified example of the valve seat member of FIG. 8. FIG. 10 is a sectional view showing the configuration of a second modified example of the valve seat member of FIG. 8.

The flow rate regulating valve 2 of this embodiment has a configuration in which a cylindrical rectifying member 20 is further added to the flow rate regulating valve 1 of the first embodiment described above. In the following description, components having the same (substantially the same) configuration as the flow rate regulating valve 1 of the first embodiment are given the same reference numerals and the description thereof will be omitted.

As shown in FIGS. 6 to 8, the flow rate adjustment valve 1 includes a valve body 10, a flow regulating member 20, a valve body 40, a can 50, a guide stem 60, a valve shaft 70, a connection mechanism 78, It has a magnet rotor 80 and a stator 90.

The flow regulating member 20 includes a cylindrical main body 21, a disk part 22 that closes the lower end of the main body 21, and an annular plate-shaped flange 23 provided at the upper end of the main body 21 so as to protrude outward in the radial direction. and integrally have. The inner diameter of the main body portion 21 is such that it can be inserted into the outer diameter side of the cylindrical portion 14 of the valve seat member 11 without any gap. The outer diameter of the main body portion 21 is smaller than the inner diameter of the second conduit 7. The disc portion 22 is provided with a plurality of refrigerant flow holes 22a.

The cylindrical portion 14 of the valve seat member 11 is inserted into the main body portion 21 of the rectifying member 20, and the disc portion 22 is arranged to face the cylindrical portion 14 in the direction of the axis L with a space therebetween. That is, the rectifying member 20 is placed over the cylindrical portion 14 . The flange portion 23 is inserted into the annular groove 17 and is sandwiched between the second conduit 7 inserted into the annular groove 17 and the valve seat member 11 . The inner circumferential surface of the main body portion 21 becomes a third circumferential surface that is substantially connected to the second tapered surface 35 and has a larger diameter than the second circumferential surface 33 .

The flow rate adjustment valve 2 of the second embodiment also has the same effects as the flow rate adjustment valve 1 of the first embodiment described above.

9 and 10 show a modification of the valve seat member 11 covered with the rectifying member 20. As shown in FIG. FIG. 9 shows a configuration in which a rectifying member 20 is placed over the valve seat member 11A shown in FIG. FIG. 10 shows a configuration in which a rectifying member 20 is placed over the valve seat member 11B shown in FIG.

Although the embodiments of the present invention have been described above, the present invention is not limited to these examples. The present invention may include additions, deletions, or design changes to the above-described embodiments by those skilled in the art as appropriate, or combinations of features of the embodiments as appropriate, as long as they do not go against the spirit of the present invention. included in the range.

The present inventor verified the effects of the present invention using the following examples and comparative examples of the present invention.

(Verification 1)
In Verification 1, the inventor verified the effect of the annular plane of the valve port on noise.

The present inventor produced electric valves having the configurations of Example 1 and Comparative Example 1 shown below. Example 1 has an annular plane. Comparative Example 1 does not have an annular plane.

(Example 1)
Example 1 is the electric valve (flow rate adjustment valve 1) of the first embodiment described above, and includes a valve port 30 having the following configuration.
Diameter D1 of first circumferential surface = 1.6 mm
Diameter D2 of second circumferential surface = 1.9mm
Outer diameter D3 of annular plane = 4.0mm
Outer diameter of cylindrical part D4 = 5.4mm
Inner diameter D5 of second conduit = 6.35mm
Length of the first circumferential surface L1 = 0.3 mm
Length L2 of the second circumferential surface = 4.6 mm
Second tapered surface length L3 = 0.9mm
Taper angle θ1 of the first tapered surface = 80 degrees Taper angle θ2 of the second taper surface = 60 degrees

(Comparative example 1)
Comparative Example 1 has the same configuration as Example 1 except that the annular plane in Example 1 is omitted. That is, Comparative Example 1 has a configuration in which D2=D3=1.9 mm in Example 1.

In Example 1 and Comparative Example 1, the inventors set the opening degree of the valve port so that a predetermined amount of refrigerant flows. A sound level meter was installed at a location approximately 15 to 30 cm away from Example 1 and Comparative Example 1 and at the location where the noise was the loudest. In Example 1 and Comparative Example 1, the differential pressure between the first conduit side and the second conduit side was set to a predetermined pressure, and the pressure was adjusted in the first direction (first conduit → valve chamber → valve port → second conduit) and in the second direction ( The noise was measured by flowing the refrigerant through the second conduit → valve port → valve chamber → first conduit. Table 1 shows the noise of Example 1 (in other words, the value obtained by subtracting the noise of Example 1 from the noise of Comparative Example 1) when the measured noise (noise measurement value) of Comparative Example 1 is used as a reference value. A negative value indicates that the noise generated by the electric valve is lower than in Comparative Example 1.

As shown in Table 1, when the noise of Comparative Example 1 is taken as the reference value, the noise of Example 1 is -1.5 dB when the refrigerant flows in the first direction, and when the refrigerant flows in the second direction, the noise of Example 1 is -1.5 dB. It became -2.1dB. In Example 1, the measured noise values were lower than in Comparative Example 1 in all cases.

When the refrigerant flows in the first direction, in Comparative Example 1, when the refrigerant reaches the second tapered surface from the second circumferential surface, the diameter of the refrigerant flow path increases continuously, the refrigerant pressure decreases, and the flow rate of the refrigerant increases. do. As a result, it is considered that in Comparative Example 1, cavitation was likely to occur and noise could not be reduced. On the other hand, in Example 1, when the refrigerant reaches the annular plane from the second circumferential surface, the diameter of the refrigerant flow path increases stepwise, and the corner between the annular plane and the second tapered surface (the corner between the annular plane and the second A small turbulent flow (vortex) is generated in the refrigerant at the connection point with the surface), reducing the flow velocity of the refrigerant. As a result, it is considered that in Example 1, the occurrence of cavitation was suppressed and noise was reduced.

When the refrigerant flows in the second direction, in Comparative Example 1, the refrigerant flows along the second tapered surface and smoothly gathers at the center of the refrigerant flow path, increasing the flow rate of the refrigerant. As a result, it is considered that in Comparative Example 1, cavitation was likely to occur and noise could not be reduced. Furthermore, in Comparative Example 1, when the small bubbles contained in the refrigerant gather smoothly in the center of the refrigerant flow path, they combine with each other and grow into large bubbles, causing noise when they burst. On the other hand, in Example 1, when the refrigerant flows along the second tapered surface and hits the annular plane, the flow velocity of the refrigerant decreases and small bubbles contained in the refrigerant burst. As a result, in Example 1, it is thought that the occurrence of cavitation and the growth of bubbles were suppressed, thereby reducing noise.

(Verification 2)
In Verification 2, the inventor verified the range of the ratio D2/D1 between the diameter D1 of the first circumferential surface and the diameter D2 of the second circumferential surface in which noise can be effectively reduced.

The present inventor manufactured an electric valve in which the diameter D2 of the second circumferential surface was changed stepwise from 1.60 mm to 2.60 mm in Example 1 described above (the configuration was the same as in Example 1 except for the diameter D2). Then, as in Verification 1, the inventor installed a sound level meter, set the differential pressure between the first conduit side and the second conduit side to a predetermined pressure, and measured the noise by flowing the refrigerant. Noise was measured, and the value obtained by subtracting the reference value from the noise measurement value was defined as the evaluation value E [dB]. The standard value was set at 55 dB (Reference: Environmental standards related to noise (Ministry of the Environment Announcement 54, March 30, 2012, "Daytime standard value for areas used exclusively and mainly for residential use: 55 dB or less") ).The flow direction of the refrigerant is the first direction.The results are shown in Table 2 and FIG.

As shown in Table 2 and FIG. 11, when the ratio D2/D1 was within the range of 1.01 to 1.55, the evaluation value E was a negative value, and the measured noise value was lower than the reference value. In particular, when the ratio D2/D1 was within the range of 1.13 to 1.38, the measured noise value was 1.8 dB or more lower than the reference value. On the other hand, when the ratio D2/D1 was 1.00 or the ratio D2/D1 was 1.63, the evaluation value E was 0 or more, and the measured noise value was more than the reference value. This result shows that the ratio D2/D1 is preferably within the range of 1.01 to 1.55, and more preferably the ratio D2/D1 is within the range of 1.13 to 1.38.

(Verification 3)
In Verification 3, the inventor verified the range of the taper angle θ1 of the first tapered surface that can effectively reduce noise.

The present inventor changed the taper angle θ1 of the first tapered surface in steps from 50 to 130 degrees in the above-mentioned Example 1, and the ratio of the diameter D1 of the first circumferential surface to the diameter D2 of the second circumferential surface (D2 /D1) was changed to 1.01, 1.19, and 1.15 (same configuration as Example 1 except for taper angle θ1 and diameter D2). Then, the present inventor measured the noise in the same manner as Verification 2, and set the value obtained by subtracting the reference value from the noise measurement value as the evaluation value E [dB]. The flow direction of the refrigerant is the first direction. The results are shown in Table 3 and FIG. 12.

As shown in Table 3 and Figure 12, when the taper angle θ1 is within the range of 60 to 120 degrees, the evaluation value E becomes a negative value regardless of the ratio D2/D1, and the measured noise value is lower than the reference value. became. In particular, when the taper angle θ1 was within the range of 70 to 100 degrees, the measured noise value was significantly lower (approximately 0.7 dB or more) than the reference value. On the other hand, when the taper angle θ1 was 50 degrees or 130 degrees, the evaluation value E was equal to or greater than 0 regardless of the ratio D2/D1, and the measured noise value was equal to or greater than the reference value. When the taper angle θ1 is 50 degrees or less, the flow velocity of the refrigerant increases and cavitation tends to occur. When the taper angle θ1 is 130 degrees or more, the turbulence of the refrigerant becomes large. Therefore, it is thought that the noise could not be reduced. This result shows that the taper angle θ1 is preferably within the range of 60 to 120 degrees, and more preferably the taper angle θ1 is within the range of 70 to 100 degrees.

(Verification 4)
In Verification 4, the inventor verified the range of the taper angle θ2 of the second tapered surface that can effectively reduce noise.

The present inventor changed the taper angle θ2 of the second tapered surface in steps from 30 to 160 degrees in the above-mentioned Example 1, and the ratio of the diameter D1 of the first circumferential surface to the diameter D2 of the second circumferential surface (D2 /D1) was changed to 1.01, 1.19, and 1.15 (the same configuration as Example 1 except for the taper angle θ2 and the diameter D2. However, the taper angle θ2 was 150 degrees and 160 degrees. In this case, the length L3 of the second tapered surface was 0.17 mm and 0.11 mm.) Then, the present inventor measured the noise in the same manner as Verification 2, and set the value obtained by subtracting the reference value from the noise measurement value as the evaluation value E [dB]. The flow direction of the refrigerant is the first direction. The results are shown in Table 4 and FIG. 13.

As shown in Table 4 and FIG. 13, when the taper angle θ2 is within the range of 40 to 150 degrees, the evaluation value E is a negative value no matter what the ratio D2/D1 is, and the measured noise value is lower than the standard value. became. In particular, when the taper angle θ2 was within the range of 60 to 100 degrees, the measured noise value was 0.7 dB or more lower than the reference value. On the other hand, when the taper angle θ2 was 30 degrees or 160 degrees, the evaluation value E was a positive value regardless of the ratio D2/D1, and the measured noise value was larger than the reference value. When the taper angle θ2 is 30 degrees or less, the flow velocity of the refrigerant increases and cavitation tends to occur. When the taper angle θ2 is 160 degrees or more, the turbulence of the refrigerant becomes large. Therefore, it is thought that the noise could not be reduced. This result shows that the taper angle θ2 is preferably within the range of 40 to 150 degrees, and more preferably the taper angle θ2 is within the range of 60 to 100 degrees.

(Verification 5)
In Verification 5, the inventor verified the range of the ratio L2/L1 between the length L1 of the first tapered surface and the length L2 of the second tapered surface that can effectively reduce noise.

The present inventor produced an electric valve in which the length L2 of the second tapered surface was changed stepwise from 0.3 to 80.0 mm in Example 1 described above (same configuration as Example 1 except for length L2). ). Then, the present inventor measured the noise in the same manner as Verification 2, and set the value obtained by subtracting the reference value from the noise measurement value as the evaluation value E [dB]. The flow direction of the refrigerant is the first direction. The results are shown in Table 5 and FIG.

As shown in Table 5 and FIG. 14, when the ratio L2/L1 is within the range of 2.0 to 133.3 (length L2 is 0.6 to 40.0 mm), the evaluation value E becomes a negative value, The noise measurement value has become lower than the standard value. In particular, when the ratio L2/L1 was within the range of 10.0 to 30.0 (length L2 was 3.0 to 9.0 mm), the measured noise value was 0.7 dB or more lower than the reference value. On the other hand, if the ratio L2/L1 is 1.0 (length L2 is 0.3 mm) or the ratio L2/L1 is 160.0 or more (length L2 is 48.0 mm or more), the evaluation value E is 0 or more. The measured noise value exceeded the standard value. If the length L2 is as short as the length L1, the refrigerant pressure will decrease stepwise at relatively short intervals, making it impossible to effectively suppress the occurrence of cavitation. If the length L2 is too long, the flow of the refrigerant in the annular plane changes rapidly from a relatively stable state, and the vortex generated in the annular plane increases. Therefore, it is thought that the noise could not be reduced. This result shows that the ratio L2/L1 is preferably within the range of 2.0 to 133.3, and more preferably the ratio L2/L1 is within the range of 10.0 to 30.0. Further, it is preferable that the ratio L2/D1 is within the range of 0.4 to 25.0 (length L2 is 0.6 to 40.0 mm), and the ratio L2/D1 is 1.9 to 5.6 (length L2 is 0.6 to 40.0 mm). It can also be seen that it is more preferable that the length L2 is within the range of 3.0 to 9.0 mm).

(Verification 6)
In Verification 6, the inventor verified the range of the length L1 of the first tapered surface that can effectively reduce noise.

The present inventor omitted the second circumferential surface, the annular plane, and the second tapered surface in Example 1 described above, and changed the length L1 of the first tapered surface stepwise from 0.1 to 1.0 mm. An electrically operated valve was produced (the diameter D1, the diameter D2 (the maximum diameter of the first tapered surface), the outer diameter D4, the inner diameter D5, and the angle θ1 were the same as in Example 1). Then, the present inventor measured the noise in the same manner as Verification 1, and set the value obtained by subtracting the reference value from the noise measurement value as the evaluation value E [dB]. In Verification 6, the reference value was set to 65 dB because the noise reduction effect was reduced because the second circumferential surface, annular plane, and second tapered surface were omitted. The flow direction of the refrigerant is the first direction. The results are shown in Table 6 and FIG. 15.

As shown in Table 6 and FIG. 15, when the length L1 was within the range of 0.2 to 0.8 mm, the evaluation value E was a negative value, and the measured noise value was lower than the reference value. In particular, when the length L1 was within the range of 0.3 to 0.6 mm, the measured noise value was 0.5 dB or more lower than the reference value. On the other hand, when the length L1 was 0.1 mm or more than 0.9 mm, the evaluation value E became a positive value, and the measured noise value became larger than the reference value. This result shows that the length L1 is preferably within the range of 0.2 to 0.8 mm, and more preferably the length L1 is within the range of 0.3 to 0.6 mm.

DESCRIPTION OF SYMBOLS 1... Flow rate adjustment valve, 6... First conduit, 7... Second conduit, 10... Valve main body, 11, 11A, 11B... Valve seat member, 12... Bottom wall part, 12a... Upper surface, 12b... Lower surface, 13... Surrounding wall Part, 14... Cylindrical part, 15... Valve chamber, 16... Valve seat, 17... Annular groove, 18... Case member, 20... Rectifying member, 21... Main body part, 22... Disc part, 22a... Refrigerant flow hole, 23 ...Flange portion, 30, 30A, 30B... Valve port, 31... First circumferential surface, 32... First tapered surface, 33, 33A, 33B... Second circumferential surface, 33A1, 33B1... First circumferential surface portion, 33A2, 33B2... intermediate tapered surface, 33A3, 33B3... second circumferential surface portion, 34... annular plane, 35... second tapered surface, 40... valve body, 50... can, 60... guide stem, 61... guide portion, 62... valve Shaft support part, 63...flange-shaped disk, 65...female thread part, 70...valve stem, 71...upper end part, 75...male thread part, 78...coupling mechanism, 80...magnetic rotor, 81...peripheral wall part, 82...ceiling part , 90... Stator, L... Axis line, D1... Diameter of the first circumferential surface, D2... Diameter of the second circumferential surface, D3... Outer diameter of the annular plane, L1... Length in the axial direction of the first circumferential surface, L2... Length in the axial direction of the second circumferential surface, L21... Length in the axial direction of the first circumferential surface portion, L22... Length in the axial direction of the intermediate tapered surface, L23... Length in the axial direction of the second circumferential surface portion , L3... Length in the axial direction of the second tapered surface, θ1... Taper angle of the first tapered surface, θ2... Taper angle of the second tapered surface

Claims (8)

An electrically operated valve having a valve body provided with a valve chamber and a valve port, and a valve body disposed to face the valve port,
The valve port is
a first peripheral surface;
a first tapered surface that is disposed further from the valve chamber than the first circumferential surface and whose diameter increases as the distance from the valve chamber increases;
a second circumferential surface that is disposed further from the valve chamber than the first tapered surface and has a larger diameter than the first circumferential surface;
an annular plane disposed further from the valve chamber than the second circumferential surface and perpendicular to the axial direction;
a second tapered surface that is disposed further from the valve chamber than the annular plane and whose diameter increases as the distance from the valve chamber increases ;
An electric valve characterized in that the following formula (A) is satisfied, where the diameter of the first circumferential surface is D1, the diameter of the second circumferential surface is D2, and the outer diameter of the annular plane is D3.
(D3-D2)>(D2-D1)... (A) The electric valve according to claim 1, wherein the length of the second circumferential surface in the axial direction is longer than the length of the first circumferential surface in the axial direction. According to claim 1 or claim 2, the following formula (1) is satisfied, where the length in the axial direction of the first circumferential surface is L1, and the length in the axial direction of the second circumferential surface is L2. electric valve.
2≦L2/L1≦133.3... (1) The electric valve according to any one of claims 1 to 3, which satisfies the following formula (2) when the diameter of the first circumferential surface is D1.
0.4≦L2/D1≦25... (2) The electric valve according to any one of claims 1 to 4, which satisfies the following formula (3), where the diameter of the first circumferential surface is D1 and the diameter of the second circumferential surface is D2. .
1.01≦D2/D1≦1.55 (3) Any one of claims 1 to 5, wherein the following formulas (4) and (5) are satisfied, where the taper angle of the first tapered surface is θ1 and the taper angle of the second tapered surface is θ2. Electric valve described in.
60 degrees≦θ1≦120 degrees... (4)
40 degrees≦θ2≦150 degrees... (5) According to any one of claims 1 to 4 and 6, the second peripheral surface has a plurality of peripheral surface portions whose diameter gradually increases as the distance from the valve chamber side increases. electric valve. a cylindrical can attached to the valve body;
a magnetic rotor housed in the can;
The electric valve according to any one of claims 1 to 7, comprising a cylindrical stator into which the can is fitted.

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