CN113251160A

CN113251160A - Electric valve

Info

Publication number: CN113251160A
Application number: CN202110076092.1A
Authority: CN
Inventors: 猪野泰利
Original assignee: Fujikoki Corp
Current assignee: Fujikoki Corp
Priority date: 2020-01-28
Filing date: 2021-01-20
Publication date: 2021-08-13
Also published as: JP7074374B2; JP2022090042A; JP7374522B2; JP2021116924A

Abstract

The invention provides an electric valve which can effectively reduce noise generated when a refrigerant flows at a valve port. In a flow rate control valve (1), a valve port (30) provided in a valve seat member (11) 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 connected in this order from the valve chamber (15) side, wherein the diameter of the first tapered surface (32) increases as the distance from the valve chamber (15) increases, the diameter of the second peripheral surface (33) is larger than the diameter of the first peripheral surface (31), the annular flat surface (34) is orthogonal to the axis L direction, and the diameter of the second tapered surface (35) increases as the distance from the valve chamber (15) increases.

Description

Electric valve

Technical Field

The present invention relates to an electric valve such as a flow rate adjustment valve for adjusting a flow rate of a refrigerant in, for example, a heat pump type cooling and heating system.

Background

Patent document 1 discloses a flow rate control valve as a conventional motor-operated valve. The flow rate control valve of patent document 1 includes a valve chamber and a valve port in a valve body. The aperture of the valve port increases in three stages or more in order as the valve chamber is separated from the valve chamber. Therefore, the noise generated when the refrigerant passes through the valve port is reduced.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2017-89864

However, according to the system using the electric valve, further reduction of noise is required.

Disclosure of Invention

Accordingly, an object of the present invention is to provide an electrically operated valve capable of effectively reducing noise generated when a 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 in the valve chamber so as to face the valve port, wherein the valve port has a first peripheral surface, a first tapered surface, a second peripheral surface, an annular flat surface, and a second tapered surface, which are sequentially connected in an axial direction from the valve chamber side, wherein a diameter of the first tapered surface increases as the valve chamber is separated from the valve chamber, a diameter of the second peripheral surface is larger than a diameter of the first peripheral surface, the annular flat surface is orthogonal to the axial direction, and a diameter of the second tapered surface increases as the valve chamber is separated 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, it is preferable that the following expression (1) is satisfied where L1 denotes a length of the first circumferential surface in the axial direction and L2 denotes a length of the second circumferential surface in the axial direction:

2≤L2/L1≤133.3…(1)

in the present invention, it is preferable that the following formula (2) is satisfied where D1 is the diameter of the first circumferential surface:

0.4≤L2/D1≤25…(2)

in the present invention, it is preferable that the following expression (3) is satisfied where D1 denotes the diameter of the first circumferential surface and D2 denotes the diameter of the second circumferential surface:

1.01≤D2/D1≤1.55…(3)

in the present invention, it is preferable that the following expressions (4) and (5) are satisfied where θ 1 denotes a taper angle of the first taper surface and θ 2 denotes a taper angle of the second taper surface:

theta 1 is more than or equal to 60 degrees and less than or equal to 120 degrees … (4)

Theta 2 is more than or equal to 40 degrees and less than or equal to 150 degrees … (5)

In the present invention, the second peripheral surface may have a plurality of peripheral surface portions having diameters gradually increasing as being distant from the valve chamber side.

In order to achieve the above object, a motor-operated valve according to another aspect of the present invention 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, wherein the valve port has a first peripheral surface and a first tapered surface that are sequentially connected in an axial direction from the valve chamber side, the first tapered surface having a diameter that increases as the valve port is separated from the valve chamber, and a second peripheral surface, an annular flat surface that is disposed at a distance from the valve chamber than the first tapered surface and has a diameter that is larger than that of the first peripheral surface, and a second tapered surface that is sequentially connected in the axial direction from the valve chamber side, the annular flat surface being orthogonal to the axial direction, the second tapered surface having a diameter that increases as the valve chamber is separated from the valve chamber.

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

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, or (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 having diameters gradually increasing as the intermediate peripheral surfaces move away from the valve chamber are arranged.

In the present invention, it is preferable that the following expression (1) is satisfied where L1 denotes a length of the first circumferential surface in the axial direction and L2 denotes a length between the first tapered surface and the annular flat surface:

2≤L2/L1≤133.3…(1)

0.4≤L2/D1≤25…(2)

in the present invention, the present invention may further include: a cylindrical can attached to the valve main body; a magnetic rotor housed in the tank; and a cylindrical stator in which the tank is fitted inside.

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

Drawings

Fig. 1 is a sectional view showing a configuration of a flow rate control valve according to a first embodiment of the present invention.

Fig. 2 is an enlarged sectional view showing a valve seat member of the flow rate control valve of fig. 1 and its vicinity.

Fig. 3 is a cross-sectional view of a valve seat member of the flow regulating valve of fig. 1.

Fig. 4 is a cross-sectional view showing a structure of a modification of the valve seat member of fig. 3.

Fig. 5 is a cross-sectional view showing a structure of another modification of the valve seat member of fig. 3.

Fig. 6 is a sectional view showing the structure of a flow rate control valve according to a second embodiment of the present invention.

Fig. 7 is an enlarged cross-sectional view showing a valve seat member of the flow rate adjustment valve of fig. 6 and its vicinity.

Fig. 8 is a cross-sectional view of a valve seat member of the flow regulating valve of fig. 6.

Fig. 9 is a cross-sectional view showing a structure of a modification of the valve seat member of fig. 8.

Fig. 10 is a cross-sectional view showing a structure of another modification of the seat member of fig. 8.

FIG. 11 is a graph showing the relationship between the ratio D2/D1 and the evaluation value E.

Fig. 12 is a graph showing a relationship between the taper angle θ 1 of the first taper surface and the evaluation value E.

Fig. 13 is a graph showing a relationship between the taper angle θ 2 of the second tapered surface and the evaluation value E.

Fig. 14 is a graph showing a relationship between the length L2 of the second peripheral surface and the evaluation value E.

Fig. 15 is a graph showing a relationship between the length L1 of the first peripheral surface and the evaluation value E.

Description of the symbols

1 … flow rate control valve, 6 … first conduit, 7 … second conduit, 10 … valve body, 11A, 11B … valve seat member, 12 … bottom wall portion, 12a … upper surface, 12B … lower surface, 13 … peripheral wall portion, 14 … cylindrical portion, 15 … valve chamber, 16 … valve seat, 17 … annular groove, 18 … housing member, 20 … rectifying member, 21 … body portion, 22 … circular plate portion, 22a … refrigerant flow hole, 23 … flange portion, 30A, 30B … valve port, 31 … first peripheral surface, 32 … first conical surface, 33A, 33B … second peripheral surface, 33A1, 33B1 … first peripheral surface portion, 33A2, 33B2 intermediate, 33A2, 33B2 second peripheral surface portion, 34 annular flat surface, 35 2, 40B 2 valve body, 2 guide portion, 2

guide

2, 2 guide portion, 2 guide portion, 65 … female screw portion, 70 … valve shaft, 71 … upper end portion, 75 … male screw portion, 78 … coupling mechanism, 80 … magnetic rotor, 81 … peripheral wall portion, 82 … top portion, 90 … stator, L … axis, D1 … first peripheral surface diameter, D2 … second peripheral surface diameter, D3 … annular plane outer diameter, L1 … first peripheral surface length in axial direction, L2 … second peripheral surface length in axial direction, L21 … first peripheral surface portion length in axial direction, L22 … intermediate tapered surface length in axial direction, L23 … second peripheral surface portion length in axial direction, L3 … second tapered surface length in axial direction, θ 1 … first tapered surface taper angle, θ 2 … second tapered surface taper angle

Detailed Description

(first embodiment)

A flow rate control valve according to a first embodiment of the present invention will be described below with reference to fig. 1 to 5.

Fig. 1 is a sectional view (a sectional view along an axis) showing a structure of a flow rate control valve according to a first embodiment of the present invention. Fig. 2 is an enlarged sectional view showing a valve seat member of the flow rate control valve of fig. 1 and its vicinity. In fig. 1 and 2, the valve body and the coupling mechanism are not cross-sectional but have shapes when viewed from the front. Fig. 3 is a cross-sectional view of a valve seat member of the flow regulating valve of fig. 1. Fig. 4 is a cross-sectional view showing a configuration of a first modification of the valve seat member of fig. 3. Fig. 5 is a sectional view showing a structure of a second modification of the valve seat member of fig. 3. In the following description, "upper and lower" indicates a positional relationship in each drawing, and does not indicate an absolute positional relationship of each component.

The flow rate adjustment valve 1 of the present embodiment is an electrically operated valve for adjusting the flow rate of a refrigerant as a fluid in, for example, a heat pump type cooling and heating system.

As shown in fig. 1 to 3, the flow rate control valve 1 includes a valve main body 10, a valve body 40, a tank 50, a guide sleeve 60, a valve shaft 70, a coupling mechanism 78, a magnet rotor 80, and a stator 90.

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

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

The valve seat member 11 is joined to the case member 18 by brazing in a state where the peripheral wall portion 13 is inserted into the lower end portion of the cylindrical case member 18. Valve seat member 11 and housing member 18 form valve chamber 15. A first conduit 6 that penetrates in a direction orthogonal to the axis L and is connected to the valve chamber 15 is joined to the housing member 18. The peripheral wall portion 13 has an effect of rectifying the flow of the refrigerant flowing from the first pipe 6 into the valve port 30 described later along the axial direction to reduce noise.

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 has a diameter that decreases with distance 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 circumferential surface of the annular groove 17 on the inner edge side becomes the outer circumferential surface of the cylindrical portion 14. The cylindrical portion 14 is inserted into the upper end portion of the second conduit 7 by inserting the upper end portion of the second conduit 7 into the annular groove 17. The bottom wall portion 12 and the second pipe 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 having a circular cross section and extending linearly. The valve chamber 15 side opening of the valve port 30 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 connected in this order from the valve chamber 15 side in the direction of the axis L.

The first circumferential surface 31 is a cylindrical circumferential surface facing radially inward. For example, the diameter D1 of the first circumferential surface 31 is 1.6mm, and the length L1 in the direction of the axis L 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 radially inward and has a diameter that increases with distance from the valve chamber 15. For example, the taper angle θ 1 of the first taper surface 32 is 80 degrees. The taper angle, also called the apex angle, is the angle formed by two generatrices in one axial section of the cone.

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

The annular flat surface 34 is a circular annular flat surface orthogonal to the direction of the axis L. The inner diameter of the annular flat surface 34 is equal to the diameter D2 of the second peripheral surface 33. The annular flat surface 34 has an outer diameter D3 greater than the diameter D2 of the second circumferential surface 33. For example, the outer diameter D3 of the annular flat surface is 4.0 mm.

The second tapered surface 35 is a conical tapered surface that is radially inward and has a diameter that increases with distance from the valve chamber 15. For example, the taper angle θ 2 of the second tapered surface 35 is 60 degrees, and the length L3 in the direction of the axis L of the second tapered surface 35 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.

Further, the valve port 30 may be modified as follows. That is, the valve port 30 has a first peripheral surface 31 and a first tapered surface 32 which are connected in order from the valve chamber 15 side in the direction of the axis L, and has a second peripheral surface 33, an annular flat surface 34, and a second tapered surface 35 which are connected in order from the valve chamber 15 side in the direction of the axis L. 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)

0.2mm＜L1＜0.8mm…(6)

The flow rate control valve according to the present invention preferably satisfies all of the above equations (1) to (6), but may satisfy 1 or more, or 2 or more, of the above equations (1) to (6).

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

The main body 41 is formed in a cylindrical shape. The outer peripheral surface of the seating portion 42 is a conical tapered surface that faces radially outward and has a diameter that decreases toward the valve port 30 (downward). In the present embodiment, the tip portion 43 has a shape for obtaining a characteristic similar to the equal percentage characteristic as the flow rate characteristic. The distal end portion 43 has conical tapered surface portions 43A to 43E (reference numerals 43B, 43C, and 43D are not shown) in multiple stages (5 stages in this case). The tapered surfaces 43A to 43E have a gradually increasing taper angle as they approach the tip end, in a manner simulating an elliptical surface. In the present specification, an angle that is half the taper angle of the tapered surface portions 43A to 43E (i.e., an intersection angle of a generatrix of the tapered surface portion and a line parallel to the axis of the valve body 40 (wherein the intersection angle is a minor angle)) is referred to as a tilt angle. This inclination angle is also referred to as a conical generatrix angle. The inclination angle θ a of the tapered surface portion 43A at the uppermost stage closest to the seating portion 42 is usually set to 3 ° < θ a < 15 ° (5 ° in this case). The lowest tapered surface 43E located farthest from the seating portion 42 is a conical surface having a sharp tip. The tip portion 43 may have a shape for obtaining a linear characteristic as a flow rate characteristic.

The valve body 40 is disposed in the valve chamber 15 such that the tip end portion 43 and the valve port 30 face each other in the direction of the axis L and the axis of the valve body 40 coincides with the axis L. The valve element 40 moves in the direction of the axis L so as to advance and retreat with respect to the valve seat 16. The seating portion 42 closes the valve port 30 when in contact with the valve seat 16. The valve element 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 tank 50 is fixed to the upper end of the housing member 18 of the valve main body 10 by welding or the like.

The guide sleeve 60 includes a valve shaft support portion 62 and a cylindrical guide portion 61, and the valve shaft support portion 62 is connected to an upper end of the guide portion 61 and is provided with a female screw portion 65. The guide portion 61 is fixed to the upper end of the case member 18 by welding or the like via a flange-like circular plate 63. The guide sleeve 60 is disposed so as to straddle the inside of the case member 18 and the inside of the tank 50.

The valve shaft 70 is formed in a cylindrical shape. The outer peripheral surface of the valve shaft 70 is provided with an external thread portion 75 that is screwed with the internal thread portion 65 of the guide rod 60. The lower end of the valve shaft 70 is coupled to the valve body 40 via a cylindrical coupling 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 magnetic 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 top portion 82 that closes the upper end of the peripheral wall portion 81. The magnetic rotor 80 is rotatably housed inside the tank. The top 82 is attached to the upper end 71 of the valve shaft 70. The valve shaft 70 rotates with the magnetic rotor 80.

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

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

In the flow rate control valve 1, when the stator 90 is energized to rotate the magnetic rotor 80 in one direction, the valve shaft 70 rotates together with the magnetic rotor 80. The valve shaft 70 and the magnet rotor 80 move downward by the screw feeding action of the female screw portion 65 of the guide collar 60 and the male screw portion 75 of the valve shaft 70, and the valve body 40 comes into contact with the valve seat 16 (valve-closed state).

Alternatively, in the flow rate control valve 1, when the stator 90 is energized to rotate the magnetic rotor 80 in the other direction, the valve shaft 70 rotates together with the magnetic rotor 80. The valve shaft 70 and the magnet rotor 80 move upward by the thread feeding action of the female thread portion 65 of the guide bush 60 and the male thread portion 75 of the valve shaft 70, and the valve body 40 is separated from the valve seat 16 (valve-opened state).

As described above, according to the flow rate control valve 1 of the present embodiment, the valve port 30 provided in the valve seat member 11 includes the first peripheral surface 31, the first tapered surface 32, the second peripheral surface 33, the annular flat surface 34, and the second tapered surface 35 which are connected in this order from the valve chamber 15 side, in which the diameter of the first tapered surface 32 increases as the distance from the valve chamber 15 increases, the diameter of the second peripheral surface 33 is larger than the diameter of the first peripheral surface 31, the annular flat surface 34 is orthogonal to the axis L direction, and the diameter of the second tapered surface 35 increases as the distance from the valve chamber 15 increases. With this arrangement, noise generated when the refrigerant flows through the valve port 30 can be effectively reduced.

In the configuration in which the end portion of the second peripheral surface 33 is connected to the second tapered surface 35 via the annular flat surface 34, the portion of the valve port 30 located forward of the end portion of the second peripheral surface 33 is expanded in diameter relative to the second peripheral surface 33 by the annular flat surface 34 and the second tapered surface 35. This structure is referred to as the former structure. On the other hand, in the configuration in which the end portion of the second peripheral surface 33 is directly connected to the second tapered surface 35, the portion of the valve port 30 ahead of the end portion of the second peripheral surface 33 is expanded in diameter with respect to the second peripheral surface 33 only by the second tapered surface 35. This structure is referred to as the latter structure. Therefore, when the diameters of the former and latter structures are expanded to the same size at the same taper angle θ 2, the length of the second taper surface 35 in the direction of the axis L can be made shorter in the former structure than in the latter structure. Thus, in the former structure, the length of the second tapered surface 35 in the direction of the axis L is short, and accordingly the length of the second peripheral surface 33 in the direction of the axis L can be made long. Therefore, the flow rate control valve 1 of the present embodiment having the former structure can reduce the flow velocity of the refrigerant in the second peripheral surface 33 regardless of the direction in which the refrigerant flows through the valve port 30, and can effectively reduce noise.

Further, when the refrigerant flows from the second duct 7 to the first duct 6, the bubbles in the refrigerant are crushed and miniaturized at the corner between the second peripheral surface 33 and the annular flat surface 34, and therefore, the noise can be effectively reduced. At this time, the second tapered surface 35 forms a flow from the radially outer side toward the radially inner side, collects bubbles in the refrigerant, and increases the speed of the refrigerant passing through the corner portion, thereby promoting the miniaturization of the bubbles.

In the above embodiment, the valve seat member 11 has the configuration in which the second peripheral surface 33 has the same diameter D2 throughout the entire axial line L direction, but the present invention is not limited to this configuration. Instead of the valve seat member 11, for example, a valve seat member 11A (fig. 4) according to a first modification having a second circumferential surface 33A and a plurality of circumferential surface portions on the second circumferential surface 33A, or a valve seat member 11B (fig. 5) according to a second modification having a second circumferential surface 33B and a plurality of circumferential surface portions on the second circumferential surface 33B may be employed. In fig. 4 and 5, the same components as those of the valve seat member 11 are denoted by the same reference numerals, and description thereof is omitted. A modified example 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 as 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 this order from the valve chamber 15 side.

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

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 has a diameter that increases with distance 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 33A 1. The second circumferential surface portion 33a3 is connected to the annular flat surface 34. The length L2 in the axis L direction of the second circumferential surface 33A (i.e., the sum of the length L21 in the axis L direction of the first circumferential surface portion 33A1, the length L22 in the axis L direction of the intermediate tapered surface 33A2, and the length L23 in the axis L direction of the second circumferential surface portion 33A 3) is longer than the length L1 in the axis L direction of the first circumferential surface 31. In addition, the length L21 in the direction of the axis L of the first circumferential surface portion 33a1 is longer than the length L23 in the direction of the axis L of the second circumferential surface portion 33 A3.

(second modification of the first embodiment)

The valve seat member 11B shown in fig. 5 is provided with a valve port 30B as 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 this order from the valve chamber 15 side.

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

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 has a diameter that increases with distance 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 greater than the diameter D21 of the first circumferential surface portion 33B 1. The second circumferential surface portion 33B3 is connected to the annular flat surface 34. The length L2 in the axis L direction of the second circumferential surface 33B (i.e., the sum of the length L21 in the axis L direction of the first circumferential surface portion 33B1, the length L22 in the axis L direction of the intermediate tapered surface 33B2, and the length L23 in the axis L direction of the second circumferential surface portion 33B 3) is longer than the length L1 in the axis L direction of the first circumferential surface 31. In addition, the length L21 in the direction of the axis L of the first circumferential surface portion 33B1 is substantially the same as the length L23 in the direction of the axis L of the second circumferential surface portion 33B 3.

In each modification of the first embodiment, the length L2 is also the length between the first tapered surface 32 and the annular flat surface 34. The

valve ports

30A and 30B also preferably satisfy one or more of the above equations (1) to (6). The modifications also have the same operational advantages as the flow rate adjustment valve 1 of the first embodiment described above.

The second circumferential surface 33A of the first modification and the second circumferential surface 33B of the second modification may have three or more circumferential surface portions whose diameters become larger in stages as they become farther from the valve chamber 15.

The valve port 30A of the first modification can be modified as follows. That is, the valve port 30A has a first peripheral surface 31 and a first tapered surface 32 which are connected in order from the valve chamber 15 side in the direction of the axis L, and has a second peripheral surface portion 33a3 (second peripheral surface), an annular flat surface 34, and a second tapered surface 35 which are connected in order from the valve chamber 15 side in the direction of the axis L. Further, a first peripheral surface portion 33a1 (one intermediate peripheral surface) is disposed between the first tapered surface 32 and the second peripheral surface portion 33A3 (alternatively, instead of the one intermediate peripheral surface, a plurality of intermediate peripheral surfaces may be disposed, the diameters of which become larger in stages as they become farther from the valve chamber 15. the diameter of the intermediate peripheral surface is larger than that of the first peripheral surface 31 and smaller than that of the second peripheral surface portion 33 A3). 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 33a 2. The valve port 30B of the second modification can be modified in the same manner as described above.

(second embodiment)

A flow rate control valve according to a second embodiment of the present invention will be described below with reference to fig. 6 to 10.

Fig. 6 is a sectional view (a sectional view along the axis) showing the structure of a flow rate control valve according to a second embodiment of the present invention. Fig. 7 is an enlarged cross-sectional view showing a valve seat member of the flow rate adjustment valve of fig. 6 and its vicinity. In fig. 6 and 7, the valve body and the coupling mechanism are not cross-sectional but have shapes when viewed from the front. Fig. 8 is a cross-sectional view of a valve seat member of the flow regulating valve of fig. 6. Fig. 9 is a cross-sectional view showing a configuration of a first modification of the valve seat member of fig. 8. Fig. 10 is a cross-sectional view showing a structure of a second modification of the valve seat member of fig. 8.

The flow rate control valve 2 of the present embodiment has a structure in which a cylindrical flow regulating member 20 is further added to the flow rate control valve 1 of the first embodiment described above. In the following description, the same reference numerals are given to constituent elements having the same (including substantially the same) configurations as those of the flow rate control valve 1 of the first embodiment, and the description thereof is omitted.

As shown in fig. 6 to 8, the flow rate control valve 1 includes a valve main body 10, a flow control member 20, a valve body 40, a tank 50, a guide sleeve 60, a valve shaft 70, a coupling mechanism 78, a magnet rotor 80, and a stator 90.

The flow regulating member 20 integrally includes a cylindrical body portion 21, a circular plate portion 22 closing a lower end of the body portion 21, and a circular plate-shaped flange portion 23 protruding radially outward from an upper end of the body portion 21. The inner diameter of the main body portion 21 is a dimension of the outer diameter side of the cylindrical portion 14 into which the valve seat member 11 is inserted without a gap. The outer diameter of the 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 22 a.

The main body portion 21 of the flow regulating member 20 is inserted inside the cylindrical portion 14 of the valve seat member 11, and the disc portion 22 is disposed so as to face the cylindrical portion 14 at a distance in the direction of the axis L. That is, the rectifying member 20 covers the cylindrical portion 14. The flange portion 23 is inserted into the annular groove 17 and sandwiched between the second pipe 7 press-fitted into the annular groove 17 and the valve seat member 11. The inner peripheral surface of the body portion 21 is a third peripheral surface substantially connected to the second tapered surface 35 and having a larger diameter than the second peripheral surface 33.

The flow rate control valve 2 of the second embodiment also has the same operational advantages as the flow rate control valve 1 of the first embodiment described above.

Fig. 9 and 10 show a modified example of the valve seat member 11 covered with the flow regulating member 20. Fig. 9 shows a structure in which the valve seat member 11A shown in fig. 4 is covered with the flow regulating member 20. Fig. 10 shows a structure in which the valve seat member 11B shown in fig. 5 is covered with a flow regulating member 20.

The embodiments of the present invention have been described above, but the present invention is not limited to these examples. A person skilled in the art can add, delete, and modify the components of the above-described embodiments as appropriate, and can combine the features of the embodiments as appropriate without departing from the spirit of the present invention, and the scope of the present invention is also encompassed by the present invention.

The present inventors have verified the effects of the present invention using examples and comparative examples of the present invention shown below.

(verification 1)

In the verification 1, the present inventors verified the effect of the annular flat surface of the valve port on noise.

The present inventors fabricated a motor-operated valve having the structure of example 1 and comparative example 1 shown below. Example 1 has a ring-shaped flat surface. Comparative example 1 does not have an annular flat surface.

(example 1)

Embodiment 1 is the electrically operated valve (flow rate adjustment valve 1) of the first embodiment described above, and includes a valve port 30, and the valve port 30 has the following structure:

the diameter D1 of the first peripheral surface is 1.6mm

The diameter D2 of the second peripheral surface is 1.9mm

Outer diameter D3 of annular plane 4.0mm

The outer diameter D4 of the cylindrical portion was 5.4mm

The second conduit has an internal diameter D5 of 6.35mm

The length L1 of the first peripheral surface is 0.3mm

The length L2 of the second peripheral surface is 4.6mm

The length L3 of the second conical surface is 0.9mm

The taper angle theta 1 of the first conical surface is 80 degrees

The taper angle theta 2 of the second taper surface is 60 degrees

Comparative example 1

Comparative example 1 has the same structure as in example 1, except that the annular flat surface is omitted in example 1. That is, in example 1, D2-D3-1.9 mm was used.

The present inventors set the opening degree of the valve port so that a predetermined amount of refrigerant flows in example 1 and comparative example 1. A noise meter is installed at a position which is separated from the example 1 and the comparative example 1 by about 15-30 cm and has the largest noise. In example 1 and comparative example 1, noise was measured by causing refrigerant to flow in a first direction (first conduit → valve chamber → second conduit) and a second direction (second conduit → valve chamber → first conduit) while setting a differential pressure between the first conduit side and the second conduit side to a predetermined pressure. Table 1 shows the noise of example 1 (in other words, a 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 motor-operated valve is lower than that of comparative example 1.

TABLE 1

Unit: dB

As shown in table 1, the noise of example 1, when the noise of comparative example 1 was used as the reference value, was-1.5 dB when the refrigerant flowed in the first direction, and was-2.1 dB when the refrigerant flowed in the second direction. In example 1, the noise measurement value was lower than that of comparative example 1 in any case.

In the case where the refrigerant flows in the first direction, in comparative example 1, when the refrigerant reaches the second taper surface from the second peripheral surface, the diameter of the refrigerant flow path is continuously enlarged, the refrigerant pressure is decreased, and the flow velocity of the refrigerant is increased. It is thus considered that cavitation is likely to occur in comparative example 1, and noise cannot be reduced. On the other hand, in example 1, when the refrigerant reaches the annular flat surface from the second peripheral surface, the diameter of the refrigerant flow path is increased stepwise, and a small turbulent flow (vortex) is generated in the corner portion between the annular flat surface and the second tapered surface (the connecting portion between the annular flat surface and the second tapered surface), and the flow velocity of the refrigerant is reduced. It is thus considered that in example 1, the generation of cavitation is suppressed and the noise can be reduced.

In the case where 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. It is thus considered that cavitation is likely to occur in comparative example 1, and noise cannot be reduced. In comparative example 1, when small bubbles contained in the refrigerant smoothly gather at the center of the refrigerant flow path, they join with each other and grow into large bubbles, and noise is generated at the time of collapse. On the other hand, in embodiment 1, when the refrigerant flows along the second tapered surface to collide with the annular flat surface, the flow velocity of the refrigerant decreases, and the small bubbles contained in the refrigerant collapse. It is thus considered that in example 1, the generation of cavitation and the growth of bubbles are suppressed, and the noise can be reduced.

(verification 2)

In the verification 2, the present inventors verified the range of the ratio D2/D1 of the diameter D1 of the first circumferential surface to the diameter D2 of the second circumferential surface, which can effectively reduce noise.

The present inventors produced an electrically operated valve in which the diameter D2 of the second peripheral surface was changed stepwise from 1.60mm to 2.60mm in example 1 described above (the same configuration as in example 1 except for the diameter D2). The present inventors also provided a noise meter in the same manner as in test 1, and measured the noise by flowing the refrigerant while setting the differential pressure between the first pipe side and the second pipe side to a predetermined pressure. Noise is measured, and a value obtained by subtracting the reference value from the noise measurement value is used as the evaluation value E [ dB ]. The reference value is 55dB (reference: environmental reference concerning noise (environmental province is equivalent to the 24-year, 3-month, 30-day notice 54, and reference value of daytime in the region dedicated to and mainly used for housing: 55dB or less)). The flow direction of the refrigerant is the first direction. The results are shown in table 2 and fig. 11.

TABLE 2

Diameter D2[ mm]	1.60	1.62	1.80	1.90	2.00	2.20	2.40	2.48	2.60
										Ratio D2/D1	1.00	1.01	1.13	1.19	1.25	1.38	1.50	1.55	1.63
Evaluation value E [ dB ]]	0.0	-0.5	-1.8	-2.2	-1.9	-1.8	-0.6	-0.4	1.0

As shown in table 2 and fig. 11, when the ratio D2/D1 is in the range of 1.01 to 1.55, the evaluation value E is a negative value, and the noise measurement value is lower than the reference value. Particularly, when the ratio D2/D1 is in the range of 1.13-1.38, the measured noise value is 1.8dB 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 is a value of 0 or more and the noise measurement value is a reference value or more. From these results, 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 the verification 3, the present inventors verified the range of the taper angle θ 1 of the first tapered surface that can effectively reduce noise.

The inventors of the present invention have made an electrically operated valve in which the taper angle θ 1 of the first tapered surface is changed stepwise from 50 to 130 degrees in the above-described embodiment 1, and the ratio (D2/D1) of the diameter D1 of the first peripheral surface to the diameter D2 of the second peripheral surface is changed to 1.01, 1.19, and 1.15 (the same configuration as that of embodiment 1 except for the taper angle θ 1 and the diameter D2). The present inventors measured noise in the same manner as in verification 2, and determined that the noise measurement value is subtracted from the reference 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.

TABLE 3

Unit: dB

As shown in table 3 and fig. 12, when the taper angle θ 1 is in the range of 60 to 120 degrees, the evaluation value E is negative regardless of the value of the ratio D2/D1, and the noise measurement value is lower than the reference value. Particularly, when the taper angle θ 1 is in the range of 70 to 100 degrees, the measured noise value is significantly lower than the reference value (approximately 0.7dB or more). On the other hand, when the taper angle θ 1 is 50 degrees or the taper angle θ 1 is 130 degrees, the evaluation value E is a value of 0 or more regardless of which value the ratio D2/D1 is, and the noise measurement value is a reference value or more. When the taper angle θ 1 is 50 degrees or less, the flow velocity of the refrigerant increases, and cavitation is likely to occur. When the taper angle θ 1 is 130 degrees or more, the refrigerant is greatly disturbed. Therefore, it is considered that noise cannot be reduced. From the results, it is found that the taper angle θ 1 is preferably in the range of 60 to 120 degrees, and the taper angle θ 1 is more preferably in the range of 70 to 100 degrees.

(verification 4)

In the verification 4, the present inventors verified the range of the taper angle θ 2 of the second tapered surface capable of effectively reducing noise.

The present inventors have made motor-operated valves in which the taper angle θ 2 of the second taper surface was changed stepwise from 30 to 160 degrees in example 1 described above and the ratio (D2/D1) of the diameter D1 of the first peripheral surface to the diameter D2 of the second peripheral surface was changed to 1.01, 1.19, and 1.15 (the same construction as in example 1 except for the taper angle θ 2 and the diameter D2, however, when the taper angle θ 2 was 150 degrees and 160 degrees, the length L3 of the second taper surface was set to 0.17mm and 0.11 mm.). The present inventors measured noise in the same manner as in verification 2, and determined that the noise measurement value is subtracted from the reference 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.

TABLE 4

Unit: dB

As shown in table 4 and fig. 13, when the taper angle θ 2 is in the range of 40 to 150 degrees, the evaluation value E is negative regardless of the value of the ratio D2/D1, and the noise measurement value is lower than the reference value. Particularly, when the taper angle theta 2 is in the range of 60-100 degrees, the measured noise value is lower than the reference value by more than 0.7 dB. On the other hand, when the taper angle θ 2 is 30 degrees or the taper angle θ 2 is 160 degrees, the evaluation value E is a positive value regardless of which value the ratio D2/D1 is, and the noise measurement value is larger than the reference value. When the taper angle θ 1 is 30 degrees or less, the flow velocity of the refrigerant increases and cavitation tends to occur. When the taper angle θ 2 is 160 degrees or more, the refrigerant is greatly disturbed. Therefore, it is considered that noise cannot be reduced. From the results, it is found that the taper angle θ 2 is preferably in the range of 40 to 150 degrees, and the taper angle θ 2 is more preferably in the range of 60 to 100 degrees.

(verification 5)

In the verification 5, the present inventors verified the range of the ratio L2/L1 of the length L1 of the first tapered surface to the length L2 of the second tapered surface, which can effectively reduce noise.

The present inventors produced an electrically operated valve in which the length L2 of the second tapered surface was changed stepwise from 0.3 to 80.0mm in example 1 described above (the same configuration as in example 1 except for the length L2). The present inventors measured noise in the same manner as in verification 2, and determined that the noise measurement value is a 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. 14.

TABLE 5

As shown in Table 5 and FIG. 14, when the ratio L2/L1 is in the range of 2.0 to 133.3 (the length L2 is 0.6 to 40.0mm), the evaluation value E is negative, and the noise measurement value is lower than the reference value. Particularly, when the ratio L2/L1 is in the range of 10.0 to 30.0 (the length L2 is 3.0 to 9.0mm), the measured noise value is lower than the reference value by 0.7dB or more. On the other hand, when the ratio L2/L1 is 1.0 (length L2 is 0.3mm) or the ratio L2/L1 is 160.0 or more (length L2 is 48.0mm or more), the evaluation value E is 0 or more and the noise measurement value is the reference value or more. If the length L2 is as short as the length L1, the refrigerant pressure decreases stepwise at short intervals, and cavitation cannot be effectively suppressed. When the length L2 is too long, the flow of the refrigerant in the annular plane changes rapidly from a relatively stable state, and the swirl generated in the annular plane becomes large. Therefore, it is considered that noise cannot be reduced. From these results, 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. It is also found that the ratio L2/D1 is preferably in the range of 0.4 to 25.0 (length L2 is 0.6 to 40.0mm), and the ratio L2/D1 is more preferably in the range of 1.9 to 5.6 (length L2 is 3.0 to 9.0 mm).

(verification 6)

In verification 6, the present inventors verified the range of the length L1 of the first tapered surface that can effectively reduce noise.

The inventors of the present invention omitted the second peripheral surface, the annular flat surface, and the second tapered surface in example 1 described above, and produced an electric valve (having the same configuration as in example 1, including 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 θ 1) in which the length L1 of the first tapered surface was changed stepwise from 0.1 to 1.0 mm. The present inventors measured noise in the same manner as in verification 1, and determined that the noise measurement value is a value obtained by subtracting the reference value from the noise measurement value as the evaluation value E [ dB ]. Further, in the verification 6, since the second peripheral surface, the annular flat surface, and the second tapered surface are omitted, the noise reduction effect is reduced, and therefore the reference value is set to 65 dB. The flow direction of the refrigerant is the first direction. The results are shown in table 6 and fig. 15.

TABLE 6

Length L1[ mm]	0.1	0.2	0.3	0.4	0.5	0.6	0.7	0.8	0.9	1.0
											Evaluation value E [ dB ]]	0.5	-0.2	-0.6	-0.6	-0.5	-0.5	-0.4	-0.2	0.1	0.5

As shown in table 6 and fig. 15, when the length L1 is in the range of 0.2 to 0.8mm, the evaluation value E is negative, and the noise measurement value is lower than the reference value. Particularly, when the length L1 is within the range of 0.3-0.6 mm, the noise measurement value is lower than the reference value by more than 0.5 dB. On the other hand, when the length L1 is 0.1mm or the length L1 is 0.9mm or more, the evaluation value E is a positive value, and the noise measurement value is larger than the reference value. From these results, it is found that the length L1 is preferably in the range of 0.2 to 0.8mm, and the length L1 is more preferably in the range of 0.3 to 0.6 mm.

Claims

1. An electrically operated valve having: 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, wherein the valve body is characterized in that,

the valve port is provided with a first peripheral surface, a first conical surface, a second peripheral surface, an annular plane and a second conical surface which are sequentially connected along the axial direction from the side of the valve chamber,

the diameter of the first tapered surface becomes larger as it goes away from the valve chamber,

the diameter of the second peripheral surface is larger than that of the first peripheral surface,

the annular plane is orthogonal to the axial direction,

the diameter of the second tapered surface becomes larger as it is farther from the valve chamber.

2. Electrically operated valve according to claim 1,

the axial length of the second circumferential surface is longer than the axial length of the first circumferential surface.

3. Electrically operated valve according to claim 1 or 2,

when the axial length of the first circumferential surface is L1 and the axial length of the second circumferential surface is L2, the following expression (1) is satisfied:

2≤L2/L1≤133.3…(1)。

4. electrically operated valve according to one of the claims 1 to 3,

when the diameter of the first circumferential surface is D1, the following expression (2) is satisfied:

0.4≤L2/D1≤25…(2)。

5. electrically operated valve according to one of the claims 1 to 4,

when the diameter of the first circumferential surface is D1 and the diameter of the second circumferential surface is D2, the following formula (3) is satisfied:

1.01≤D2/D1≤1.55…(3)。

6. electrically operated valve according to one of the claims 1 to 5,

when the taper angle of the first taper surface is defined as θ 1 and the taper angle of the second taper surface is defined as θ 2, the following expressions (4) and (5) are satisfied:

theta 1 is more than or equal to 60 degrees and less than or equal to 120 degrees … (4),

theta 2 is more than or equal to 40 degrees and less than or equal to 150 degrees … (5).

7. Electrically operated valve according to one of the claims 1 to 4 and 6,

the second peripheral surface has a plurality of peripheral surface portions gradually increasing in diameter as it goes away from the valve chamber side.

8. An electrically operated valve having: 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, wherein the valve body is characterized in that,

the valve port has a first peripheral surface and a first tapered surface which are connected in order in an axial direction from the valve chamber side, the first tapered surface having a diameter which increases with distance from the valve chamber, and,

the valve device includes a second peripheral surface, an annular flat surface, and a second tapered surface, the second peripheral surface, the annular flat surface, and the second tapered surface being sequentially connected in an axial direction from the valve chamber side, the second peripheral surface being disposed farther from the valve chamber than the first tapered surface, and having a larger diameter than the first peripheral surface, the annular flat surface being orthogonal to the axial direction, and the second tapered surface having a larger diameter as the second peripheral surface is farther from the valve chamber.

9. Electrically operated valve according to claim 8,

the first tapered surface is connected to the second peripheral surface.

10. Electrically operated valve according to claim 8,

between the first tapered surface and the second peripheral surface,

an 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 provided, or,

a plurality of intermediate peripheral surfaces are arranged, each of which has a diameter larger than that of the first peripheral surface, is smaller than that of the second peripheral surface, and has a diameter gradually increasing with increasing distance from the valve chamber.

11. Electrically operated valve according to one of the claims 8 to 10,

when the axial length of the first circumferential surface is L1 and the axial length between the first tapered surface and the annular flat surface is L2, the following expression (1) is satisfied:

2≤L2/L1≤133.3…(1)。

12. electrically operated valve according to claim 11,

0.4≤L2/D1≤25…(2)。

13. electrically operated valve according to one of the claims 1 to 12,

comprising:

a cylindrical can attached to the valve main body;

a magnetic rotor housed in the tank; and

and a cylindrical stator in which the tank is fitted inside.