JP7074374B2 - Solenoid valve - Google Patents

Description

The present invention relates to, for example, an electric valve such as a flow rate adjusting valve used for adjusting the flow rate of a refrigerant in a heat pump type heating / cooling system or the like.

Patent Document 1 discloses a flow rate adjusting valve which is an example of a conventional electric valve. The flow rate adjusting valve of Patent Document 1 is provided with a valve chamber and a valve opening in the valve body. Then, the diameter of the valve opening 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 opening.

Japanese Unexamined Patent Publication No. 2017-89864

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

Therefore, an object of the present invention is to provide an electric valve capable of effectively reducing the noise generated when the refrigerant flows through the valve opening.

In order to achieve the above object, the electric valve according to one aspect of the present invention includes a valve body provided with a valve chamber and a valve opening, and a valve body arranged in the valve chamber so as to face the valve opening. The valve port is an electric valve having, the first peripheral surface connected in order from the valve chamber side in the axial direction, and the first tapered surface whose diameter increases as the distance from the valve chamber increases. It is characterized by having a second peripheral surface having a diameter larger than that of the first peripheral surface, an annular plane orthogonal to the axial direction, and a second tapered surface whose diameter increases as the distance from the valve chamber increases.

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

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

In the present invention, when the diameter of the first peripheral surface is D1, it is preferable to satisfy the following formula (2).
0.4 ≤ L2 / D1 ≤ 25 ... (2)

In the present invention, when the diameter of the first peripheral surface is D1 and the diameter of the second peripheral surface is D2, it is preferable to satisfy the following formula (3).
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 to satisfy the following equations (4) and (5).
60 degrees ≤ θ1 ≤ 120 degrees ... (4)
40 degrees ≤ θ2 ≤ 150 degrees ... (5)

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

In order to achieve the above object, the electric valve according to another aspect of the present invention includes a valve body provided with a valve chamber and a valve opening, and a valve arranged in the valve chamber so as to face the valve opening. An electric valve having a body, the valve port is a first peripheral surface connected in order from the valve chamber side in the axial direction, and a first tapered surface whose diameter increases as the distance from the valve chamber increases. A second peripheral surface having It is characterized by having an annular plane orthogonal to the axial direction and a second tapered surface whose diameter increases as the distance from the valve chamber increases.

In the present invention, the first tapered surface and the second peripheral surface may be connected to each other.

In the present invention, between the first tapered surface and the second peripheral surface, (a) one intermediate peripheral surface having a diameter larger than that of the first peripheral surface and a diameter smaller than that of the second peripheral surface is arranged. Alternatively, (b) a plurality of intermediate peripheral surfaces having a diameter larger than that of the first peripheral surface and a diameter smaller than that of the second peripheral surface and gradually increasing in diameter as the distance from the valve chamber is increased are arranged. It may have been done.

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

In the present invention, when the diameter of the first peripheral surface is D1, it is preferable to satisfy the following formula (2).
0.4 ≤ L2 / D1 ≤ 25 ... (2)

In the present invention, it may have a cylindrical can attached to the valve body, a magnet rotor housed in the can, and a tubular stator in which the can is fitted inward.

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

It is sectional drawing which shows the structure of the flow rate control valve which concerns on 1st Embodiment of this invention. It is an enlarged sectional view which shows the valve seat member of the flow rate control valve of FIG. 1 and the vicinity thereof. It is sectional drawing of the valve seat member of the flow rate control valve of FIG. It is sectional drawing which shows the structure of the modification of the valve seat member of FIG. It is sectional drawing which shows the structure of the other modification of the valve seat member of FIG. It is sectional drawing which shows the structure of the flow rate control valve which concerns on 2nd Embodiment of this invention. It is an enlarged sectional view which shows the valve seat member of the flow rate control valve of FIG. 6 and the vicinity thereof. It is sectional drawing of the valve seat member of the flow rate control valve of FIG. It is sectional drawing which shows the structure of the modification of the valve seat member of FIG. It is sectional drawing which shows the structure of the other modification of the valve seat member of FIG. It is a graph which shows the relationship between the ratio D2 / D1 and the evaluation value E. It is a graph which shows the relationship between the taper angle θ1 of the 1st taper surface, and the evaluation value E. It is a graph which shows the relationship between the taper angle θ2 of the 2nd taper surface, and the evaluation value E. It is a graph which shows the relationship between the length L2 of the 2nd peripheral surface, and the evaluation value E. It is a graph which shows the relationship between the length L1 of the 1st peripheral surface and the evaluation value E.

(First Embodiment)
Hereinafter, the flow rate adjusting valve according to the first embodiment of the present invention will be described with reference to FIGS. 1 to 5.

FIG. 1 is a cross-sectional view (cross-sectional view along the axis) showing the configuration of the flow rate control valve according to the first embodiment of the present invention. FIG. 2 is an enlarged cross-sectional view showing the valve seat member of the flow rate control valve of FIG. 1 and its vicinity. In FIGS. 1 and 2, the valve body and the connecting mechanism have a shape seen from the front rather than a cross section. FIG. 3 is a cross-sectional view of the valve seat member of the flow rate adjusting valve of FIG. FIG. 4 is a cross-sectional view showing the configuration of the first modification of the valve seat member of FIG. FIG. 5 is a cross-sectional view showing the configuration of the second modification of the valve seat member of FIG. In the following description, "upper and lower" indicates the positional relationship in each figure, and does not indicate the absolute positional relationship of each constituent member.

The flow rate adjusting valve 1 of the present embodiment is an electric valve used for adjusting the flow rate of the refrigerant as a fluid in, for example, a heat pump type heating / cooling system.

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

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

The valve seat member 11 is manufactured by cutting a metal material such as stainless steel, for example. The valve seat member 11 has a disk-shaped bottom wall portion 12, a cylindrical peripheral wall portion 13 extending upward from the upper surface 12a of the bottom wall portion 12, and a cylinder extending downward from the lower surface 12b of the bottom wall portion 12. It has a portion 14 integrally.

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 portion 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 penetrates the case member 18 in a direction orthogonal to the axis L and is connected to the valve chamber 15 is joined to the case member 18. The peripheral wall portion 13 has the effect of reducing noise by rectifying the flow of the refrigerant flowing from the first conduit 6 into the valve port 30 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 inward in the radial direction and whose diameter decreases as the distance from the valve chamber 15 increases.

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 peripheral surface on the inner edge side of the annular groove 17 is the outer peripheral surface of the cylindrical portion 14. By inserting the upper end portion of the second conduit 7 into the annular groove 17, the cylindrical portion 14 is inserted into the upper end portion of the second conduit 7. Then, the bottom wall portion 12 and the second conduit 7 are joined by brazing.

A valve port 30 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 30 is a space having a circular cross section extending 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 has a first peripheral surface 31, a first tapered surface 32, a second peripheral surface 33, an annular flat surface 34, and a second tapered surface 35, which are sequentially connected from the valve chamber 15 side in the L direction of the axis. And have.

The first peripheral surface 31 is a cylindrical peripheral surface facing inward in the radial direction. As an example, the diameter D1 of the first peripheral surface 31 is 1.6 mm, and the length L1 in the axis L direction is 0.3 mm. The first peripheral 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 inward in the radial direction and increases in diameter as the distance from the valve chamber 15 increases. As an example, the taper angle θ1 of the first tapered surface 32 is 80 degrees. The taper angle, also called the apex angle, is the angle formed by the two generatrix of the cone in one axial cross section.

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

The annular plane 34 is a circular annular plane orthogonal to the L direction of the axis. 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 inward in the radial direction and increases in diameter as the distance from the valve chamber 15 increases. 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 axis L direction is 0.9 mm. In the present embodiment, the lower end of the second tapered surface 35 is the lower end of the cylindrical portion 14.

The valve opening 30 can be paraphrased as follows. That is, the valve port 30 has a first peripheral 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 valve chamber 15 side in the axis L direction. It has a second peripheral surface 33, an annular plane 34, and a second tapered surface 35, which are connected in order. The first tapered surface 32 and the second peripheral surface 33 are connected to each other.

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)
0.2 mm <L1 <0.8 mm ... (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 a plurality of the above formulas (1) to (6). It may be a thing.

The valve body 40 is formed in a columnar shape as a whole. The valve body 40 has a body portion 41, a seating portion 42, and a tip portion 43 connected in order from the upper side to the lower side in the axis L direction.

The body portion 41 is formed in a columnar shape. The outer peripheral surface of the seating portion 42 is a conical tapered surface that faces outward in the radial direction and whose diameter decreases toward the valve port 30 side (downward). In the present embodiment, the tip portion 43 has a shape for obtaining a characteristic similar to the equal percent characteristic as the flow rate characteristic. The tip portion 43 has a plurality of stages (here, five stages) of conical tapered surface portions 43A to 43E (reference numerals 43B, 43C, 43D are not shown). The taper angle of the tapered surface portions 43A to 43E is gradually increased as it approaches the tip so as to imitate an ellipsoidal surface. In the present specification, the inclination angle is half the angle of 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 the line parallel to the axis of the valve body 40 (however, the intersection angle is inferior angle)). That is. This tilt angle is also called the conical generatrix angle. The inclination angle θa of the uppermost tapered surface portion 43A closest to the seating portion 42 is usually set to 3 ° <θa <15 ° (here, 5 °). The lowermost tapered surface portion 43E farthest from the seating portion 42 is a conical surface with a sharp point. The tip portion 43 may adopt a shape for obtaining a linear characteristic as a flow rate characteristic.

The valve body 40 is arranged in the valve chamber 15 so that the tip portion 43 faces the valve port 30 in the axis L direction and the axis of the valve body 40 coincides with the axis L. The valve body 40 is moved in the axis L direction so as to advance and retreat with respect to the valve seat 16. The seating portion 42 closes the valve opening 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 according to the distance (lift amount) from the valve seat 16.

The can 50 is formed in a cylindrical shape with the upper end closed. 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 has 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 screw portion 65. The guide portion 61 is fixed to the upper end of the case member 18 via a flange-shaped 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 in a columnar shape. On the outer peripheral surface of the valve shaft 70, a male threaded portion 75 screwed to the female threaded portion 65 of the guide stem 60 is provided. The lower end of the valve shaft 70 is connected to the valve body 40 via a cylindrical connecting mechanism 78. The connecting mechanism 78 is slidably arranged inside the guide portion 61 in the L direction of the axis.

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

The stator 90 is formed in a substantially cylindrical shape. The can 50 is fitted inside the stator 90. The stator 90 creates a magnetic field that rotates the magnet rotor 80 in one direction and the other. The stator 90 constitutes a stepping motor together with the magnet rotor 80.

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

When the stator 90 is energized so that the magnet rotor 80 rotates in one direction in the flow rate adjusting valve 1, 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 shaft 70, the valve shaft 70 and the magnet rotor 80 move downward, and the valve body 40 comes into contact with the valve seat 16 (valve closed state). ..

Alternatively, when the stator 90 is energized so that the magnet rotor 80 rotates in the other direction in the flow rate adjusting valve 1, 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 shaft 70, the valve shaft 70 and the magnet rotor 80 move upward, and the valve body 40 separates from the valve seat 16 (valve open state). ..

From the above, according to the flow control valve 1 of the present embodiment, the valve port 30 provided in the valve seat member 11 is separated from the first peripheral surface 31 connected in order from the valve chamber 15 side and the valve chamber 15. The diameter of the first tapered surface 32 increases as the diameter increases, the second peripheral surface 33 having a diameter larger than that of the first peripheral surface 31, the annular plane 34 orthogonal to the axis L direction, and the diameter increases as the distance from the valve chamber 15 increases. It has a second tapered surface 35 and the like. Since this is done, 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 peripheral surface 33 via the annular flat surface 34, the portion of the valve port 30 beyond the end of the second peripheral surface 33 is the annular flat surface 34 and the second tapered surface. The diameter is expanded with respect to the second peripheral surface 33 by the surface 35. This configuration is called the former configuration. On the other hand, in the configuration in which the second tapered surface 35 is directly connected to the end of the second peripheral surface 33, the portion of the valve port 30 beyond the end of the second peripheral surface 33 is formed only by the second tapered surface 35. The diameter is expanded with respect to the two peripheral surfaces 33. This configuration is called the latter configuration. Therefore, when the diameter of the former configuration and the latter configuration is 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 shorter in the former configuration than in the latter configuration. In the former configuration, the length of the second peripheral surface 33 in the axis L direction can be increased by the shorter length of the second tapered surface 35 in the axis L direction. Therefore, the flow rate adjusting valve 1 of the present embodiment having the former configuration can reduce the flow velocity of the refrigerant on the second peripheral surface 33 regardless of the direction in which the refrigerant flows at the valve port 30, and is effective in noise. Can be reduced to.

Further, when the refrigerant flows from the second conduit 7 to the first conduit 6, bubbles in the refrigerant are crushed and miniaturized at the corners between the second peripheral surface 33 and the annular plane 34, so that noise is effectively reduced. Can be reduced. At this time, the second tapered surface 35 creates a flow from outward to inward in the radial direction, collects bubbles in the refrigerant, increases the speed at which the refrigerant passes through the corners, and promotes miniaturization of the bubbles. ing.

In the above-described embodiment, the valve seat member 11 has a configuration in which the second peripheral surface 33 has the same diameter D2 over the entire axis L direction, but the present invention is not limited to this configuration. Instead of the valve seat member 11, for example, the valve seat member 11A (FIG. 4) having a second peripheral surface 33A having a plurality of peripheral surface portions, or the second peripheral surface having a plurality of peripheral surface portions. The valve seat member 11B (FIG. 5) of the second modification having the surface 33B may be adopted. In FIGS. 4 and 5, the same components as those of the valve seat member 11 described above are designated 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)
The valve seat member 11A shown in FIG. 4 is provided with a valve port 30A which is a refrigerant flow path so as to penetrate the bottom wall portion 12 and the cylindrical portion 14. The valve port 30A has a first peripheral surface 31, a first tapered surface 32, a second peripheral surface 33A, an annular flat surface 34, and a second tapered surface 35, which are connected in order from the valve chamber 15 side. is doing.

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

The first peripheral surface portion 33A1 is a cylindrical peripheral surface facing inward in the radial direction. The diameter D21 of the first peripheral surface portion 33A1 is larger than the diameter D1 of the first peripheral surface 31. The first peripheral 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 inward in the radial direction and whose diameter increases as the distance from the valve chamber 15 increases. The second peripheral surface portion 33A3 is a cylindrical peripheral surface facing inward in the radial direction. The diameter D22 of the second peripheral surface portion 33A3 is larger than the diameter D21 of the first peripheral surface portion 33A1. The second peripheral surface portion 33A3 is connected to the annular plane 34. The length L2 of the second peripheral surface 33A in the axis L direction (that is, the length L21 of the first peripheral 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 peripheral surface portion 33A3. The total length L23 in the axis L direction of the first peripheral surface 31) is longer than the length L1 in the axis L direction of the first peripheral surface 31. Further, the length L21 of the first peripheral surface portion 33A1 in the axis L direction is longer than the length L23 of the second peripheral surface portion 33A3 in the axis L direction.

(Second variant 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 peripheral surface 31, a first tapered surface 32, a second peripheral surface 33B, an annular flat surface 34, and a second tapered surface 35, which are connected in order from the valve chamber 15 side. is doing.

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

The first peripheral surface portion 33B1 is a cylindrical peripheral surface facing inward in the radial direction. The diameter D21 of the first peripheral surface portion 33B1 is larger than the diameter D1 of the first peripheral surface 31. The first peripheral 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 inward in the radial direction and whose diameter increases as the distance from the valve chamber 15 increases. The second peripheral surface portion 33B3 is a cylindrical peripheral surface facing inward in the radial direction. The diameter D22 of the second peripheral surface portion 33B3 is larger than the diameter D21 of the first peripheral surface portion 33B1. The second peripheral surface portion 33B3 is connected to the annular plane 34. The length L2 of the second peripheral surface 33B in the axis L direction (that is, the length L21 of the first peripheral 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 peripheral surface portion 33B3. The total length L23 in the axis L direction of the first peripheral surface 31) is longer than the length L1 in the axis L direction of the first peripheral surface 31. Further, the length L21 of the first peripheral surface portion 33B1 in the axis L direction and the length L23 of the second peripheral 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 port 30A and the valve port 30B also satisfy one or a plurality of the above formulas (1) to (6). Each modification also has the same effect as the flow rate adjusting valve 1 of the first embodiment described above.

The second peripheral surface 33A of the first modification and the second peripheral surface 33B of the second modification have three or more peripheral surfaces whose diameters gradually increase as the distance from the valve chamber 15 increases. You may.

The valve opening 30A of the first modification can be paraphrased as follows. That is, the valve port 30A has a first peripheral 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 valve chamber 15 side in the axis L direction. It has a second peripheral surface portion 33A3 (second peripheral surface), an annular plane 34, and a second tapered surface 35, which are connected in order. Then, the first peripheral surface portion 33A1 (one intermediate peripheral surface) is arranged between the first tapered surface 32 and the second peripheral surface portion 33A3 (note that the valve is replaced with one intermediate peripheral surface). A plurality of intermediate peripheral surfaces whose diameters gradually increase as the distance from the chamber 15 increases may be arranged. The intermediate peripheral surfaces have a larger diameter than the first peripheral surface 31 and a smaller diameter than the second peripheral surface portion 33A3. be.). The first tapered surface 32 and the second peripheral surface portion 33A3 are connected via the first peripheral surface portion 33A1 and the intermediate tapered surface portion 33A2. The valve opening 30B of the second modification can be paraphrased in the same manner as described above.

(Second Embodiment)
Hereinafter, the flow rate adjusting valve according to the second embodiment of the present invention will be described with reference to FIGS. 6 to 10.

FIG. 6 is a cross-sectional view (cross-sectional view along the axis) showing the configuration of the flow rate control valve according to the second embodiment of the present invention. FIG. 7 is an enlarged cross-sectional view showing the valve seat member of the flow rate control valve of FIG. 6 and its vicinity. In FIGS. 6 and 7, the valve body and the connecting mechanism are not in cross section but in a shape seen from the front direction. FIG. 8 is a cross-sectional view of the valve seat member of the flow rate adjusting valve of FIG. FIG. 9 is a cross-sectional view showing the configuration of the first modification of the valve seat member of FIG. FIG. 10 is a cross-sectional view showing the configuration of the second modification of the valve seat member of FIG.

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

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

The rectifying member 20 includes a cylindrical main body portion 21, a disk portion 22 that closes the lower end of the main body portion 21, and a ring plate-shaped flange portion 23 provided at the upper end of the main body portion 21 so as to project outward in the radial direction. And, in an integrated manner. The inner diameter of the main body portion 21 is a dimension that is inserted without a gap on the outer diameter side of the cylindrical portion 14 of the valve seat member 11. The outer diameter of the main body 21 is smaller than the inner diameter of the second conduit 7. The disk portion 22 is provided with a plurality of refrigerant flow holes 22a.

The cylindrical portion 14 of the valve seat member 11 is inserted inside the main body portion 21 of the rectifying member 20, and the disc portion 22 is arranged so as to face the cylindrical portion 14 in the L direction of the axis at intervals. That is, the rectifying member 20 is covered with 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 peripheral surface of the main body 21 is a third peripheral surface having a diameter larger than that of the second peripheral surface 33, which is substantially connected to the second tapered surface 35.

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

9 and 10 show a configuration of a modified example of the valve seat member 11 covered with the rectifying member 20. FIG. 9 shows a configuration in which the valve seat member 11A shown in FIG. 4 is covered with the rectifying member 20. FIG. 10 shows a configuration in which the valve seat member 11B shown in FIG. 5 is covered with the rectifying member 20.

Although embodiments of the present invention have been described above, the present invention is not limited to these examples. A person skilled in the art appropriately adding, deleting, or changing the design of the above-described embodiment, or a combination of the features of the embodiment as appropriate is also the present invention as long as it does not contradict the gist of the present invention. Is included in the range of.

The present inventor has verified the action and effect of the present invention using the following examples and comparative examples of the present invention.

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

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

(Comparative Example 1)
Comparative Example 1 has the same configuration as that of Example 1 except that the annular plane is omitted in Example 1. 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 present inventor 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 about 15 to 30 cm away from Example 1 and Comparative Example 1 and at a location with the loudest noise. In Example 1 and Comparative Example 1, the differential pressure between the first conduit side and the second conduit side is set as a predetermined pressure, and the first direction (first conduit → valve chamber → valve opening → second conduit) and the second direction ( Noise was measured by flowing a refrigerant through the second conduit → valve opening → 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 of Comparative Example 1 (noise measurement value) is used as a reference value. A negative value indicates that the noise generated by the motorized valve is lower than that of Comparative Example 1.

As shown in Table 1, the noise of Example 1 when the noise of Comparative Example 1 is used as a reference value is -1.5 dB when the refrigerant flows in the first direction, and is -1.5 dB when the refrigerant flows in the second direction. It became -2.1 dB. In Example 1, the noise measurement value was lower than that of Comparative Example 1 in each case.

When the refrigerant flows in the first direction, in Comparative Example 1, when the refrigerant reaches from the second peripheral surface to the second tapered surface, the diameter of the refrigerant flow path continuously expands, the refrigerant pressure decreases, and the flow velocity of the refrigerant increases. do. As a result, in Comparative Example 1, it is probable that cavitation was likely to occur and the noise could not be reduced. On the other hand, in the first embodiment, when the refrigerant reaches the annular plane from the second peripheral surface, the diameter of the refrigerant flow path gradually increases, and the corner portion between the annular plane and the second tapered surface (annular plane and the second taper). A small turbulent flow (vortex) is generated in the refrigerant at the connection point with the surface), and the flow velocity of the refrigerant decreases. As a result, in Example 1, it is considered that the occurrence of cavitation was suppressed and the noise could be 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, and the flow velocity of the refrigerant increases. As a result, in Comparative Example 1, it is probable that cavitation was likely to occur and the noise could not be reduced. Further, in Comparative Example 1, when small bubbles contained in the refrigerant smoothly gather in the center of the refrigerant flow path, they combine with each other and grow into large bubbles, which causes noise at the time of bursting. On the other hand, in the first embodiment, 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 considered that the generation of cavitation and the growth of air bubbles were suppressed, and the noise could be reduced.

(Verification 2)
In the verification 2, the present inventor verified the range of the ratio D2 / D1 between the diameter D1 of the first peripheral surface and the diameter D2 of the second peripheral surface that can effectively reduce the noise.

The present inventor produced an electric valve in which the diameter D2 of the second peripheral surface was changed stepwise from 1.60 mm to 2.60 mm in Example 1 described above (the same configuration as in Example 1 except for the diameter D2). Then, the present inventor installed a sound level meter in the same manner as in Verification 1, and measured the noise by flowing the refrigerant with the differential pressure between the first conduit side and the second conduit side as a predetermined pressure. The noise was measured, and the value obtained by subtracting the reference value from the measured noise value was defined as the evaluation value E [dB]. The standard value was 55 dB (Reference: Environmental standard for noise (Ministry of the Environment, March 30, 2012, Circular 54, "Daytime standard value for areas exclusively and mainly used for housing: 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 in the range of 1.01 to 1.55, the evaluation value E became a negative value, and the noise measurement value became lower than the reference value. In particular, when the ratio D2 / D1 was in the range of 1.13 to 1.38, the noise measurement value was 1.8 dB or more lower than the reference value. On the other hand, when the ratio D2 / D1 is 1.00 or the ratio D2 / D1 is 1.63, the evaluation value E becomes a value of 0 or more, and the noise measurement value becomes a reference value or more. From this result, it can be seen that the ratio D2 / D1 is preferably in the range of 1.01 to 1.55, and the ratio D2 / D1 is more preferably in the range of 1.13 to 1.38.

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

In the first embodiment described above, the present inventor changes the taper angle θ1 of the first tapered surface stepwise from 50 to 130 degrees, and the ratio of the diameter D1 of the first peripheral surface to the diameter D2 of the second peripheral surface (D2). An electric valve in which / D1) was changed to 1.01, 1.19 and 1.15 was produced (the same configuration as in Example 1 except for the taper angle θ1 and the diameter D2). Then, the present inventor measured the noise in the same manner as in the verification 2, and set the value obtained by subtracting the reference value from the measured noise 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.

As shown in Table 3 and FIG. 12, when the taper angle θ1 is in the range of 60 to 120 degrees, the evaluation value E becomes a negative value regardless of the ratio D2 / D1, and the noise measurement value is lower than the reference value. became. In particular, when the taper angle θ1 was in the range of 70 to 100 degrees, the noise measurement value was significantly (generally 0.7 dB or more) lower than the reference value. On the other hand, when the taper angle θ1 is 50 degrees or the taper angle θ1 is 130 degrees, the evaluation value E becomes 0 or more regardless of the ratio D2 / D1, and the noise measurement value becomes the reference value or more. When the taper angle θ1 is 50 degrees or less, the flow velocity of the refrigerant increases and cavitation is likely to occur. When the taper angle θ1 is 130 degrees or more, the turbulence of the refrigerant becomes large. Therefore, it is probable that the noise could not be reduced. From this result, it can be seen that the taper angle θ1 is preferably in the range of 60 to 120 degrees, and the taper angle θ1 is more preferably in the range of 70 to 100 degrees.

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

In the first embodiment described above, the present inventor changes the taper angle θ2 of the second tapered surface stepwise from 30 to 160 degrees, and the ratio of the diameter D1 of the first peripheral surface to the diameter D2 of the second peripheral surface (D2). Electric valves in which / D1) were changed to 1.01, 1.19 and 1.15 were produced (the same configuration as in Example 1 except for the taper angle θ2 and the diameter D2. However, the taper angles θ2 were 150 degrees and 160 degrees. At this time, the length L3 of the second tapered surface was set to 0.17 mm and 0.11 mm). Then, the present inventor measured the noise in the same manner as in the verification 2, and set the value obtained by subtracting the reference value from the measured noise 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.

As shown in Table 4 and FIG. 13, when the taper angle θ2 is in the range of 40 to 150 degrees, the evaluation value E becomes a negative value regardless of the ratio D2 / D1, and the noise measurement value is lower than the reference value. became. In particular, when the taper angle θ2 was in the range of 60 to 100 degrees, the noise measurement value was 0.7 dB or more lower than the reference value. On the other hand, when the taper angle θ2 is 30 degrees or the taper angle θ2 is 160 degrees, the evaluation value E becomes a positive value regardless of the ratio D2 / D1, and the noise measurement value becomes larger than the reference value. When the taper angle θ2 is 30 degrees or less, the flow velocity of the refrigerant increases and cavitation is likely to occur. When the taper angle θ2 is 160 degrees or more, the turbulence of the refrigerant becomes large. Therefore, it is probable that the noise could not be reduced. From this result, it can be seen that the taper angle θ2 is preferably in the range of 40 to 150 degrees, and the taper angle θ2 is more preferably in the range of 60 to 100 degrees.

(Verification 5)
In verification 5, the present inventor has verified the range of the ratio L2 / L1 of 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 (the same configuration as in Example 1 except for the length L2). ). Then, the present inventor measured the noise in the same manner as in the verification 2, and set the value obtained by subtracting the reference value from the measured noise 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 in 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 became lower than the standard value. In particular, when the ratio L2 / L1 was in the range of 10.0 to 30.0 (length L2 was 3.0 to 9.0 mm), the noise measurement value was 0.7 dB or more lower than the reference value. On the other hand, when 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. It became a value, and the noise measurement value exceeded the standard value. If the length L2 is as short as the length L1, the refrigerant pressure is gradually reduced at relatively short intervals, and the occurrence of cavitation cannot be effectively suppressed. If the length L2 is too long, the flow of the refrigerant suddenly changes from a relatively stable state in the annular plane, and the vortex generated in the annular plane becomes large. Therefore, it is probable that the noise could not be reduced. From this result, it can be seen that the ratio L2 / L1 is preferably in the range of 2.0 to 133.3, and the ratio L2 / L1 is more preferably in the range of 10.0 to 30.0. Further, the ratio L2 / D1 is preferably in 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). It can also be seen that it is more preferable that L2 is in the range of 3.0 to 9.0 mm).

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

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

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

1 ... Flow control valve, 6 ... 1st conduit, 7 ... 2nd conduit, 10 ... Valve body, 11, 11A, 11B ... Valve seat member, 12 ... Bottom wall, 12a ... Top surface, 12b ... Bottom surface, 13 ... Peripheral wall Part, 14 ... Cylindrical part, 15 ... Valve chamber, 16 ... Valve seat, 17 ... Circular groove, 18 ... Case member, 20 ... Rectifying member, 21 ... Main body part, 22 ... Disc part, 22a ... Refrigerator flow hole, 23 ... Flange portion, 30, 30A, 30B ... Valve port, 31 ... First peripheral surface, 32 ... First tapered surface, 33, 33A, 33B ... Second peripheral surface, 33A1, 33B1 ... First peripheral surface portion, 33A2, 33B2 ... Intermediate tapered surface, 33A3, 33B3 ... Second peripheral surface portion, 34 ... Circular plane, 35 ... Second tapered surface, 40 ... Valve body, 50 ... Can, 60 ... Guide stem, 61 ... Guide part, 62 ... Valve Shaft support part, 63 ... Diameter disk, 65 ... Female thread part, 70 ... Valve shaft, 71 ... Upper end part, 75 ... Male thread part, 78 ... Connection mechanism, 80 ... Magnet rotor, 81 ... Peripheral wall part, 82 ... Ceiling part , 90 ... Stator, L ... Axis line, D1 ... First peripheral surface diameter, D2 ... Second peripheral surface diameter, D3 ... Circular plane outer diameter, L1 ... First peripheral surface axial length, L2 ... Axial length of the second peripheral surface, L21 ... Axial length of the first peripheral surface portion, L22 ... Axial length of the intermediate tapered surface, L23 ... Axial length of the second peripheral surface portion , L3 ... Length in the axial direction of the second tapered surface, θ1 ... Tapered angle of the first tapered surface, θ2 ... Tapered angle of the second tapered surface

Claims (13)

An electric valve having a valve body provided with a valve chamber and a valve opening, and a valve body arranged in the valve chamber so as to face the valve opening.
The valve openings were connected in order from the valve chamber side in the axial direction.
The first peripheral surface and
A first tapered surface whose diameter increases as the distance from the valve chamber increases,
A second peripheral surface having a diameter larger than that of the first peripheral surface,
An annular plane orthogonal to the axial direction,
An electric valve characterized by having a second tapered surface whose diameter increases as the distance from the valve chamber increases. The motorized valve according to claim 1, wherein the axial length of the second peripheral surface is longer than the axial length of the first peripheral surface. The invention according to claim 1 or 2, wherein when the axial length of the first peripheral surface is L1 and the axial length of the second peripheral surface is L2, the following formula (1) is satisfied. Electric valve.
2 ≦ L2 / L1 ≦ 133.3 ・ ・ ・ (1) The motorized valve according to any one of claims 1 to 3, which satisfies the following formula (2) when the diameter of the first peripheral surface is D1.
0.4 ≤ L2 / D1 ≤ 25 ... (2) The motorized valve according to any one of claims 1 to 4, wherein the diameter of the first peripheral surface is D1 and the diameter of the second peripheral surface is D2, which satisfies the following formula (3). ..
1.01 ≤ D2 / D1 ≤ 1.55 ... (3) One of claims 1 to 5, which satisfies the following equations (4) and (5) when the taper angle of the first tapered surface is θ1 and the taper angle of the second tapered surface is θ2. The electric valve described in.
60 degrees ≤ θ1 ≤ 120 degrees ... (4)
40 degrees ≤ θ2 ≤ 150 degrees ... (5) The second peripheral surface has a plurality of peripheral surface portions whose diameters gradually increase as the distance from the valve chamber side increases, according to any one of claims 1 to 4 and 6. Electric valve. An electric valve having a valve body provided with a valve chamber and a valve opening, and a valve body arranged in the valve chamber so as to face the valve opening.
The valve port is
It has a first peripheral surface connected in order from the valve chamber side in the axial direction, and a first tapered surface whose diameter increases as the distance from the valve chamber increases.
The second peripheral surface, which is connected in order from the valve chamber side in the axial direction, is arranged away from the valve chamber from the first tapered surface and has a larger diameter than the first peripheral surface, is orthogonal to the axial direction. An electric valve characterized by having an annular flat surface and a second tapered surface whose diameter increases as the distance from the valve chamber increases. The motorized valve according to claim 8, wherein the first tapered surface and the second peripheral surface are connected to each other. Between the first tapered surface and the second peripheral surface,
(A) One intermediate peripheral surface having a diameter larger than that of the first peripheral surface and a diameter smaller than that of the second peripheral surface is arranged or arranged.
(B) A plurality of intermediate peripheral surfaces having a diameter larger than that of the first peripheral surface and a diameter smaller than that of the second peripheral surface and gradually increasing in diameter as the distance from the valve chamber is increased are arranged. 8. The electric valve according to 8. Claims 8 to 8 satisfy the following equation (1), where L1 is the axial length of the first peripheral surface and L2 is the length between the first tapered surface and the annular plane. Item 2. The electric valve according to any one of Item 10.
2 ≦ L2 / L1 ≦ 133.3 ・ ・ ・ (1) The motorized valve according to claim 11, wherein the following equation (2) is satisfied when the diameter of the first peripheral surface is D1.
0.4 ≤ L2 / D1 ≤ 25 ... (2) A cylindrical can attached to the valve body and
The magnet rotor housed in the can and
The electric valve according to any one of claims 1 to 12, further comprising a tubular stator in which the can is fitted.

Images