JP6799024B2 - Solenoid valve and refrigeration cycle system - Google Patents

Description

The present invention relates to an electric valve and a refrigeration cycle system using the electric valve.

Conventionally, an electric valve having a structure as shown in FIG. 8 has been known (see, for example, Patent Document 1). That is, when the stepping motor is driven to rotate the rotor 103, the valve body 114 moves in the valve central axis L direction, which is the central axis of the valve body 114, due to the screw feeding action of the female screw 131a and the male screw 121a. As a result, the opening degree of the valve port 130b is adjusted, and the flow rate of the fluid flowing in from the pipe joint 111 and flowing out from the pipe joint 112 or the flow rate of the fluid flowing in from the pipe joint 112 and flowing out from the pipe joint 111 is controlled. Will be done.

Here, when controlling the flow rate of various fluids, there is a problem that fluid passing noise is generated, so that noise reduction is required. Further, in the case where the electric valve 100 controls the refrigerant flow rate in the indoor unit of the refrigeration cycle of a household air conditioner or a commercial air conditioner using a refrigerant, the liquid refrigerant is a gas-liquid mixed two-phase before and after passing through the valve port 130b. Since it becomes a flow, it is required to exhibit quietness even in various refrigerant states and operating conditions.

Japanese Unexamined Patent Publication No. 2016-0898770

By the way, the above-mentioned electric valve 100 is fixed to a fluid pipe (not shown) via a pipe joint 111 and a pipe joint 112, and the valve body portion 120 and the valve port 130b of the valve seat 130 are exposed in the flow path. .. Here, the valve body portion 120 refers to a component having a valve body 114 at the lower end of the valve guide 118. The valve guide 118 holds the valve body 114 at the lower end and moves together with the valve body 114 in the valve central axis L direction.

Therefore, in the electric valve 100, when a high pressure difference occurs between the inlet side and the outlet side of the valve port 130b, particularly when the fluid flows from the pipe joint 111 to the pipe joint 112, as shown in FIG. , A fluid such as a refrigerant flowing in from the pipe joint 111 may hit the valve body portion 120, and the valve body portion 120 may vibrate in the radial direction (C) due to the collision force. When the sound generated by this vibration is generated, the quietness of the motor-operated valve 100 may not be maintained.

Therefore, as shown in FIG. 10, it is conceivable to raise the position of the top surface 130a of the valve seat 130 so that the fluid flowing from the pipe joint 111 into the valve chamber 121 does not directly hit the valve body portion 120. Be done. However, in this case, the ascending flow generated by the fluid flowing from the pipe joint 111 colliding with the valve seat 130 invades the guide portion 132 that restrains the inclination and movement of the valve body portion 120, and vibrates the valve body portion 120. May cause noise. Therefore, in this case as well, it becomes difficult to maintain quietness.

An object of the present invention is to provide an electric valve capable of accurately maintaining quietness, and a refrigeration cycle system using the electric valve.

[1] The motorized valve of the present invention
The rotary motion of the rotor housed in the inner circumference of the case is converted into a linear motion by the screw feed mechanism of the male screw member and the female screw member, and the valve body part housed in the valve body is converted based on this linear motion. An electric valve that moves in the direction of the valve central axis, which is the central axis of the valve body.
A valve chamber, which is a space formed in the valve body,
A first valve port provided on the side surface of the valve body and serving as an inlet / outlet on the valve chamber side,
A second valve port provided directly below the valve body portion in a coaxial direction with the valve body portion and capable of approaching or separating the valve body portion.
A tubular valve seat portion in which the second valve port is formed on the rotor side, and
A valve shaft holder that guides the valve body portion in the valve center axis direction,
With
When the valve body portion is closest to the valve seat portion, the maximum outer diameter of the valve body portion, which is the largest diameter on the valve seat portion side with respect to the lower end of the valve shaft holder, is the top of the valve seat portion. Larger than the outer diameter of the annular valve seat flat surface formed on the surface,
Moreover, the position of the valve seat plane portion in the valve central axis direction is located on the rotor side of the lowermost end of the inner diameter of the first valve port, which is the farthest position from the rotor.
In this way, by forming the maximum outer diameter of the valve body portion to be larger than the outer diameter of the valve seat flat portion, the fluid is obstructed by the valve body portion and between the valve body portion and the accommodating chamber for accommodating the valve body portion. It is possible to prevent the fluid from flowing into the clearance of the valve body, reduce the noise generated by the vibration of the valve body portion, and maintain the quietness accurately.

[2] Further, the motorized valve of the present invention is
The valve body is
A valve body that adjusts the flow rate of the fluid passing through the second valve port, and
Including a valve guide that holds the valve body on the valve seat side and is slidably arranged with respect to the valve shaft holder.
The valve body is fixed to the valve guide.
By fixing the valve body to the valve guide in this way, the valve body does not vibrate in the valve guide due to the fluid, and quietness can be maintained.

[3] Further, the motorized valve of the present invention is
The valve body
The needle part, which is the part closest to the second valve port, and
It is characterized by including an annular flat surface portion located on the outer periphery of the base end of the needle portion.
As a result, the valve body is urged upward by the fluid that collides with the flat surface, and the contact surface between the male and female threads in the screw feed mechanism can be kept constant and the occurrence of screw backlash is suppressed. be able to. Therefore, the quietness of the solenoid valve can be accurately maintained.

[4] Further, the motorized valve of the present invention is
A shoulder portion forming the lower end edge of the maximum outer diameter of the valve body portion is provided.
The position of the shoulder portion in the valve central axis direction is such that the valve body portion is closest to the valve seat portion and the inner diameter of the first valve port is closer to the rotor than the uppermost end. It is characterized by being located on the rotor side.
As a result, when the fluid flows in from the first valve port, the collision of the fluid with the valve body is reduced even when the valve body is closest to the valve seat, and the ascending flow is applied to the shoulder. By being hindered, it is prevented from flowing into the clearance between the valve body and the accommodation chamber accommodating the valve body.

[5] Further, the motorized valve of the present invention is
The valve seat portion is characterized by having a tapered portion whose outer diameter becomes smaller toward the rotor side.
Since the fluid is guided inside the maximum outer diameter of the valve body by this taper, it is possible to prevent the fluid from flowing into the clearance between the valve body and the accommodation chamber accommodating the valve body more accurately. , The quietness of the motorized valve is maintained.

[6] Further, the motorized valve of the present invention is
The lowermost end of the first valve port is located closer to the rotor than the inner bottom surface of the valve body.
As a result, the fluid that does not rise can flow into the lower space near the inner bottom surface of the valve body, and the fluid can be prevented from flowing into the clearance between the valve body portion and the accommodation chamber accommodating the valve body portion. ..

[7] Further, the refrigeration cycle system of the present invention is
A refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, characterized in that the above-mentioned electric valve is used as the expansion valve.

According to the present invention, it is possible to provide an electric valve capable of accurately maintaining quietness and a refrigeration cycle system using the electric valve.

It is the schematic sectional drawing of the electric valve which concerns on embodiment. It is an enlarged view of the main part of the electric valve which concerns on embodiment. FIG. 5 is an enlarged view of a main part of the motorized valve according to the embodiment in a state where the valve body portion is closest to the valve seat portion. It is an enlarged view of the main part of the electric valve which provided the tapered part in the valve seat part which concerns on another embodiment. FIG. 5 is an enlarged view of a main part of an electric valve in which a valve seat portion is integrated with a valve body according to another embodiment. FIG. 5 is an enlarged view of a main part of an electric valve in which a first valve port is formed on a side surface of a valve body according to another embodiment. FIG. 5 is an enlarged view of a main part of an electric valve in which a flat surface portion is not formed on a needle portion of a valve body portion according to another embodiment. It is the schematic sectional drawing of the conventional electric valve. It is an enlarged view of the main part of the conventional electric valve. It is an enlarged view of the main part of the electric valve as a comparative example.

Hereinafter, the motorized valve according to the embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a schematic cross-sectional view showing the motorized valve 2 according to the embodiment. In addition, in this specification, "upper" or "lower" is defined in the state of FIG. That is, the rotor 4 is located above the valve body 17.

In the motorized valve 2, the valve body 30 is integrally connected to the lower side of the opening side of the case 60 having a tubular cup shape made of metal by welding or the like.
Here, the valve body 30 is made of a metal such as stainless steel, and has a valve chamber 11 which is a space formed inside. Further, on the side surface of the valve body 30, for example, a first pipe joint 12 made of stainless steel or copper that directly communicates with the valve chamber 11 is fixedly mounted. On the valve chamber 11 side of the first pipe joint 12, a first valve port 12a having a circular cross section is formed as an inlet / outlet for fluid. Further, a valve seat portion 16 having a second valve port 16a having a circular cross section formed upward is incorporated in the inner bottom surface 30a of the valve body 30 so as to protrude from the inner bottom surface 30a. The second valve port 16a is provided in the direction coaxial with the valve body 17 directly below the valve body 17. A second pipe joint 15 made of, for example, stainless steel or copper, which communicates with the first pipe joint 12 via the second valve port 16a and the valve chamber 11, is fixedly mounted on the valve seat portion 16.

A rotatable rotor 4 is housed in the inner circumference of the case 60, and a valve shaft 41 is arranged at a shaft core portion of the rotor 4 via a bush member 33. The rotor 4 is made of a magnetic material such as a resin material containing magnetic powder or a ferrite magnet. Both the bush member 33 and the valve shaft 41 are made of a metal such as stainless steel, and the valve shaft 41 and the rotor 4 connected by the bush member 33 move integrally in the vertical direction while rotating. A male screw 41a is formed on the outer peripheral surface of the valve shaft 41 near the middle portion. In this embodiment, the valve shaft 41 functions as a male screw member. Further, the valve body 17 can be brought close to or separated from the second valve port 16a.

A stator composed of a yoke, a bobbin, a coil, and the like (not shown) is arranged on the outer periphery of the case 60, and the rotor 4 and the stator form a stepping motor.
Below the bush member 33 of the valve shaft 41, a valve shaft holder 6 having a function of forming a screw feed mechanism A with the valve shaft 41 and suppressing the inclination of the valve shaft 41 is provided as a valve body. It is fixed so that it cannot rotate relative to 30.

The valve shaft holder 6 includes a tubular small diameter portion 6a on the upper side, a tubular large diameter portion 6b on the lower side, a fitting portion 6c accommodated on the inner peripheral portion side of the valve body 30, and a ring-shaped flange portion 6f. Consists of. The flange portion 6f of the valve shaft holder 6 is fixed to the upper end of the valve body 30 by welding or the like. Further, inside the valve shaft holder 6, a storage chamber 6h for accommodating a valve guide 18 described later is formed. The valve shaft holder 6 is made of a resin material except for the metal flange portion 6f.

Further, a female screw 6d is formed downward from the upper opening 6g of the tubular small diameter portion 6a of the valve shaft holder 6 to a predetermined depth. Therefore, in the present embodiment, the valve shaft holder 6 functions as a female screw member. The screw feed mechanism A is composed of a male screw 41a formed on the outer circumference of the valve shaft 41 and a female screw 6d formed on the inner circumference of the tubular small diameter portion 6a of the valve shaft holder 6.

Further, a pressure equalizing hole 51 is formed on the side surface of the tubular large diameter portion 6b of the valve shaft holder 6, and the pressure equalizing hole 51 allows the accommodating chamber 6h in the tubular large diameter portion 6b and the rotor accommodating chamber. It communicates with 67 (second back pressure chamber). By providing the pressure equalizing hole 51 in this way, the space for accommodating the rotor 4 of the case 60 and the space inside the valve shaft holder 6 are communicated with each other, so that the valve body 17 can be smoothly moved. ..

Further, below the valve shaft 41, a tubular valve body portion 20 is slidably arranged with respect to the accommodating chamber 6h of the valve shaft holder 6. The valve body portion 20 includes a tubular valve guide 18 that slides in the accommodation chamber 6h, and a valve body 17 that adjusts the flow rate of the fluid passing through the second valve port 16a. The valve body 17 is fixed below the valve guide 18 and is held by the valve guide 18. Further, the compressed valve spring 27 and the spring receiver 35 are housed in the valve guide 18. The upper end of the spring receiver 35 is in point contact with the protruding portion 41c of the valve shaft 41.

The ceiling portion 21 side of the valve guide 18 is bent at a substantially right angle by press molding. A through hole 18a is formed in the ceiling portion 21. Further, a flange portion 41b is further formed below the valve shaft 41.

Here, the valve shaft 41 is inserted into the through hole 18a of the valve guide 18 in a loose state so as to be rotatable with respect to the valve guide 18 and displaceable in the radial direction, and the flange portion 41b is a valve. It is arranged in the valve guide 18 so as to be rotatable with respect to the guide 18 and displaceable in the radial direction. Further, the valve shaft 41 is arranged so that the through hole 18a is inserted and the upper surface of the flange portion 41b faces the ceiling portion 21 of the valve guide 18. Since the flange portion 41b has a diameter larger than that of the through hole 18a of the valve guide 18, the valve shaft 41 is prevented from coming off.

Since the valve shaft 41 and the valve guide 18 can move in the radial direction to each other, the valve guide 18 and the valve guide 18 and the valve guide 18 and the valve guide 18 are not required to have a high degree of concentric mounting accuracy with respect to the arrangement positions of the valve shaft holder 6 and the valve shaft 41. Concentricity with the valve body 17 can be obtained.
A washer 70 having a through hole formed in the central portion is installed between the ceiling portion 21 of the valve guide 18 and the flange portion 41b of the valve shaft 41.

Next, a main part of the motor-operated valve 2 according to the embodiment will be described. FIG. 2 is an enlarged view of a main part of the motor-operated valve 2 according to the embodiment. As shown in FIG. 2, the valve body 17 has a columnar fixing portion 17a fixed to the inner circumference of the valve guide 18, a substantially disk-shaped lid portion 17b that closes the lower end of the valve guide 18, and a substantially truncated cone shape. It is provided with a needle portion 17c having the shape of the above and having a function of adjusting the flow rate of the fluid passing through the second valve port 16a. The needle portion 17c is located at the lowermost position of the valve body 17.

The lid portion 17b is provided with a flat surface portion 17d which is an annular plane located on the outer periphery of the base end 17c'of the needle portion 17c protruding below the lid portion 17b. Further, on the outer periphery of the flat surface portion 17d, a shoulder portion 17e forming the lower end edge of the portion forming the maximum outer diameter X (described later) of the valve body portion 20 is formed. Further, a clearance 22 is formed between the outer circumference of the valve body portion 20 and the inner circumference of the accommodation chamber 6h of the valve shaft holder 6.

The maximum outer diameter X of the valve body portion 20 is a range below the lower end 6k of the valve shaft holder 6 in a state where the valve body portion 20 is closest to the valve seat portion 16 (see reference numeral S in FIG. 3). ) Is the part with the largest diameter. Further, a valve seat flat surface portion 16b, which is an annular flat surface, is formed on the top surface of the valve seat portion 16.

Here, the maximum outer diameter X of the valve body portion 20 is formed to be larger than the outer diameter Y of the valve seat flat surface portion 16b (X> Y). Further, the position of the valve seat flat surface portion 16b fixedly mounted on the second pipe joint 15 is the lowermost end of the inner diameter of the first valve port 12a in the valve central axis M direction which is the central axis of the valve body 17 and the valve body portion 20. It is located above P (rotor 4 side). The lowermost end P is the inner diameter of the first valve port 12a and is the farthest position from the rotor 4. Further, the lowermost end P is located above the inner bottom surface 30a in the valve body 30, and a lower space 11a surrounding the valve seat portion 16 is formed in the vicinity of the inner bottom surface 30a in the valve body 30.

When a fluid flows into the valve chamber 11 from the first pipe joint 12 through the first valve port 12a, the fluid collides with the valve seat portion 16 to cause an upward upward flow in the valve center axis M direction and the valve center. A downward downward flow in the axis M direction occurs. The ascending flow splits, a part of it collides with the flat surface portion 17d and the shoulder portion 17e and then folds downward, and the other part flows from the shoulder portion 17e to the inner side surface of the valve body 30 and becomes the valve body portion 20. The inflow into the clearance 22 of the containment chamber 6h is avoided. Further, the valve body portion 20 is urged upward by the ascending current colliding with the flat surface portion 17d. On the other hand, the downward flow flows into the lower space 11a.

Further, as shown in FIG. 3, when the valve body portion 20 is closest to the valve seat portion 16, the position R of the shoulder portion 17e in the valve central axis M direction is the uppermost end Q of the inner diameter of the first valve port 12a. It is located on the upper side (rotor 4 side). The uppermost end Q is the position closest to the rotor 4 in the inner diameter of the first valve port 12a. As a result, even when the valve body portion 20 is closest to the valve seat portion 16, the fluid flowing into the valve chamber 11 through the first valve port 12a is reduced from colliding with the valve body portion 20, and the fluid The ascending flow generated by the collision with the valve seat portion 16 is obstructed by the shoulder portion 17e, thereby preventing the fluid from flowing into the clearance 22.

According to the motorized valve 2 according to this embodiment, the valve seat portion 16 projects from the inner bottom surface 30a in the valve body 30, and the position of the valve seat flat portion 16b is the inner diameter of the first valve port 12a in the valve central axis M direction. By forming the maximum outer diameter X of the valve body portion 20 larger than the outer diameter Y of the valve seat flat surface portion 16b (X> Y) when the valve body portion 20 is located above the lowermost end P of the valve body, the ascending flow is formed in the valve body. It is prevented from flowing into the clearance 22 by being obstructed by the portion 20. Further, the valve body portion 20 is urged upward by the ascending flow that collides with the flat surface portion 17d, and the contact surface between the threads of the male screw 41a and the female screw 6d can be kept constant to prevent screw play. Can be done. Therefore, the noise generated by the vibration of the valve body portion 20 can be alleviated, and the quietness can be accurately maintained.

Further, when the valve body portion 20 is closest to the valve seat portion 16, the position R of the shoulder portion 17e in the valve center axis M direction is located above the uppermost end Q of the inner diameter of the first valve port 12a. Even in this state, the fluid flowing from the first valve port 12a is accurately prevented from flowing into the clearance 22, and the noise generated by the vibration of the valve body portion 20 can be suppressed more reliably.

Further, since the valve body 17 is fixed to the valve guide 18, the valve body 17 does not vibrate in the valve guide 18 due to the fluid, and the quietness of the motorized valve 2 can be maintained. Further, since the lower space 11a is formed in the vicinity of the inner bottom surface 30a in the valve body 30, the fluid flowing in from the first valve port 12a and branched downward can flow into the lower space 11a, and the fluid has a clearance. It is possible to prevent the fluid from flowing into the 22.

Further, in the above-described embodiment, as shown in FIG. 4, the valve seat portion 16 may have a tapered portion 16c whose outer diameter decreases upward. In this case, the ascending flow is guided inward by the tapered portion 16c with respect to the maximum outer diameter X of the valve body portion 20. Therefore, it is more accurately prevented that the ascending current flows into the clearance 22, and the quietness of the motorized valve 2 is maintained. The tapered boundary portion O of the tapered portion 16c, which is the portion where the outer circumference of the valve seat portion 16 begins to incline, is located below the lowermost end P of the inner diameter of the first valve port 12a (on the bottom surface 30a side of the valve chamber). If so, it is still preferable. In this case, the inflow of the ascending current into the clearance 22 can be more accurately avoided.

Further, in the above-described embodiment, the case where the valve seat portion 16 is incorporated as a separate component in the inner bottom surface 30a of the valve body 30 is described as an example, but as shown in FIG. 5, the valve body 30 The valve seat portion 16 may protrude from the inner bottom surface 30a of the valve body 30 and the valve seat portion 16 may be formed as an integral part. In this case, the first valve port 12a may be a different part from the first pipe joint 12. For example, as shown in FIG. 6, the first valve port 12a may be formed on the side surface of the valve body 30.

Further, in the above-described embodiment, the case where the fluid flows into the valve chamber 11 through the first valve port 12a in the forward direction is described, but the fluid is the second pipe joint 15, the valve seat portion. The fluid may flow into the valve chamber 11 in the opposite direction via the 16 and the second valve port 16a. Also in this case, the fluid collides with the flat surface portion 17d and the shoulder portion 17e and then folds downward, or flows from the shoulder portion 17e to the inner side surface of the valve body 30 and flows into the clearance 22 between the valve body portion 20 and the accommodation chamber 6h. Is avoided. Then, when the fluid collides with the flat surface portion 17d, the valve body portion 20 is urged upward.

Further, in the above-described embodiment, the flat surface portion 17d may not be formed on the lid portion 17b. For example, as shown in FIG. 7, the shoulder portion 17e may be formed at the boundary between the needle portion 17c and the outer peripheral surface of the lid portion 17b. The shoulder portion 17e forms the outer peripheral edge of the base end of the needle portion 17c protruding downward from the lid portion 17b. In this case, the area of the outer peripheral surface of the needle portion 17c is large and the inclination angle of the outer peripheral surface with respect to the valve center axis M is large, so that the fluid is guided toward the inner side surface of the valve body 30 and flows into the clearance 22. Is prevented.

Further, in the above-described embodiment, the flat surface portion 17d is assumed to be a flat surface, but may have irregularities. Further, the flat surface portion 17d does not necessarily have to be a plane orthogonal to the valve central axis M, and may be inclined with respect to a plane orthogonal to the valve central axis M.

Further, in the above-described embodiment, the shape of the needle portion 17c may be a substantially conical shape with a sharp tip.

Further, the electric valve 2 of the above-described embodiment is used as an expansion valve provided between the condenser and the evaporator in, for example, a refrigeration cycle system including a compressor, a condenser, an expansion valve, an evaporator and the like. Be done.

2 Electric valve 4 Rotor 6 Valve shaft holder 6a Cylindrical small diameter part 6b Cylindrical large diameter part 6c Fitting part 6d Female screw 6f Flange part 6g Upper opening 6h Storage chamber 6k Lower end of valve shaft holder 11 Valve chamber 11a Lower space 12 1st pipe joint 12a 1st valve port 15 2nd pipe joint 16 Valve seat part 16a 2nd valve port 16b Valve seat flat part 16c Tapered part 17 Valve body 17a Fixing part 17b Lid part 17c Needle part 17c'Base end of needle part 17d Flat surface 17e Shoulder 18 Valve guide 18a Through hole 20 Valve body 21 Ceiling 22 Clearance 27 Valve spring 30 Valve body 30a Internal bottom surface 33 Bush member 41 Valve shaft 41a Male screw 41b Flange 41c Protrusion 51 Pressure equalizing hole 60 Case 67 Rotor housing 70 Washer 100 Electric valve 103 Rotor 111 Pipe fitting 112 Pipe fitting 114 Valve body 118 Valve guide 120 Valve body 121 Valve chamber 121a Male screw 130 Valve seat 130a Top surface 130b Valve port 131a Female screw L Valve center shaft M Valve central axis O Tapered boundary P Lower end of inner diameter of 1st valve port Q Uppermost end of inner diameter of 1st valve port R Position of shoulder in axial direction X Maximum outer diameter of valve body Y Maximum outer diameter of valve seat Outer diameter

Claims (7)

The rotary motion of the rotor housed in the inner circumference of the case is converted into a linear motion by the screw feed mechanism of the male screw member and the female screw member, and the valve body part housed in the valve body is converted based on this linear motion. An electric valve that moves in the direction of the valve central axis, which is the central axis of the valve body.
A valve chamber, which is a space formed in the valve body,
A first valve port provided on the side surface of the valve body and serving as an inlet / outlet on the valve chamber side,
A second valve port provided directly below the valve body portion in a coaxial direction with the valve body portion and capable of approaching or separating the valve body portion.
A tubular valve seat portion in which the second valve port is formed on the rotor side, and
A valve shaft holder that guides the valve body portion in the valve center axis direction,
With
When the valve body portion is closest to the valve seat portion, the maximum outer diameter of the valve body portion, which is the largest diameter on the valve seat portion side with respect to the lower end of the valve shaft holder, is the top of the valve seat portion. Larger than the outer diameter of the annular valve seat flat surface formed on the surface,
Further, the motorized valve is characterized in that the position of the valve seat flat surface portion in the valve central axis direction is located on the rotor side of the lowermost end of the inner diameter of the first valve port, which is the farthest position from the rotor. The valve body is
A valve body that adjusts the flow rate of the fluid passing through the second valve port, and
Including a valve guide that holds the valve body on the valve seat side and is slidably arranged with respect to the valve shaft holder.
The electric valve according to claim 1, wherein the valve body is fixed to the valve guide. The valve body
The needle part, which is the part closest to the second valve port, and
The electric valve according to claim 2, further comprising an annular flat surface portion located on the outer periphery of the base end of the needle portion. A shoulder portion forming the lower end edge of the maximum outer diameter of the valve body portion is provided.
The position of the shoulder portion in the valve central axis direction is such that the valve body portion is closest to the valve seat portion and the inner diameter of the first valve port is closer to the rotor than the uppermost end. The electric valve according to any one of claims 1 to 3, which is located on the rotor side. The motorized valve according to any one of claims 1 to 4, wherein the valve seat portion has a tapered portion whose outer diameter becomes smaller toward the rotor side. The motorized valve according to any one of claims 1 to 5, wherein the lowermost end of the first valve port is located on the rotor side of the inner bottom surface of the valve body. A refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, wherein the electric valve according to any one of claims 1 to 6 is used as the expansion valve. ..

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