JP2021124180A - Motor-operated valve and refrigeration cycle system - Google Patents

Abstract

To stabilize operability of a motor-operated valve by suppressing deflection and inclination of a rotor shaft, in the motor-operated valve in which an opening of a valve port is controlled by a valve member by conversion to linear motion in an axial direction, of the rotor shaft by a screw feeding mechanism.SOLUTION: A screw feeding mechanism is composed of a female screw portion 21a formed on a supporting member 2 at a valve housing 1 side, and a male screw portion 3a formed on a rotor shaft 3 of a stepping motor 6. Rotary motion of a magnetic rotor 62 of the stepping motor 6 is converted into linear motion in an axis X direction of the rotor shaft 3 by the screw feeding mechanism. An opening of a valve port 11 is controlled by a needle valve 5 connected to the rotor shaft 3. A bush member 71 is disposed between a constriction portion 31 (part of rotor shaft 3) moving integrally with the rotor shaft 3 in the axis X direction, and a shaft guide hole 21b holding the rotor shaft 3 on the axis X.SELECTED DRAWING: Figure 1

Description

The present invention relates to an electric valve and a refrigeration cycle system used in a refrigeration cycle system or the like.

Conventionally, as an electric valve provided in a refrigeration cycle of an air conditioner, for example, there are those disclosed in Japanese Patent Application Laid-Open No. 2016-23711 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2017-25974 (Patent Document 2). In these electric valves, a male screw portion is formed on the rotor shaft side of the electric motor, a female screw portion through which the rotor shaft penetrates is arranged, and a valve member is provided at the lower end of the rotor shaft. Then, the rotary motion of the rotor of the electric motor is converted into a linear motion in the axial direction of the rotor shaft by the screw feed mechanism of the female screw portion and the male screw portion, and the valve member is moved to control the opening degree of the valve port. .. In Patent Document 1, a stopper mechanism for regulating the rotation range of the magnet rotor of the electric motor, that is, the lower end position and the upper end position is provided on the outer periphery of the support member having the female screw portion formed therein. Further, in Patent Document 2, a similar stopper mechanism is provided inside the ceiling of the sealed case (on the end side of the rotor shaft).

Japanese Unexamined Patent Publication No. 2016-23711 Japanese Unexamined Patent Publication No. 2017-25974

In the electric valve using the screw feed mechanism including the female screw portion and the male screw portion as described above, a clearance is required between the female screw portion and the male screw portion in consideration of the operability of the screw feed mechanism. For this reason, the rotor shaft may run out or tilt when the magnet rotor rotates, and when this runout occurs, the rotor shaft and the parts connected to the rotor shaft come into uneven contact with the sliding portion, and the electric valve. May worsen the operability of.

The present invention is a refrigeration cycle system including an electric valve that is converted into a linear motion in the axial direction of the rotor shaft by a screw feed mechanism and the opening degree of a valve port is controlled by a valve member, and a refrigeration cycle system including the electric valve. The subject is to suppress and stabilize the operability of the electric valve.

The electric valve of the present invention includes a female threaded portion formed on a support member on the valve body side and a male threaded portion formed on the rotor shaft of the electric motor and arranged through the center of the female threaded portion, and is a magnet of the electric motor. The rotary motion of the rotor is converted into a linear motion in the axial direction of the rotor shaft by the screw feed mechanism of the female screw portion and the male screw portion, and the opening degree of the valve port is controlled by the valve member connected to the rotor shaft. In the electric valve, a guided portion that moves in the axial direction integrally with the rotor shaft, and an on-axis guide hole forming a cylindrical cavity that inserts the guided portion and holds the guided portion on the axis. It is characterized by including a bush member provided between the guided portion and the shaft guide hole and lightly press-fitted into the guided portion and the shaft guide hole.

At this time, the on-axis guide hole is a shaft guide hole formed in the support member coaxially with the female screw portion, and the guided portion is a constricted portion formed coaxially with the male screw portion of the rotor shaft. An electric valve characterized by this is preferable.

Further, the on-axis guide hole is a slide hole formed in the support member coaxially with the female threaded portion, and the guided portion is integrally formed with the rotor shaft and holds the valve member. An electric valve characterized by being a valve holder arranged in the slide hole is preferable.

Further, a guide tube is provided at the end of the rotor shaft on the side opposite to the valve member to regulate the rotation range of the magnet rotor, and the end of the rotor shaft is inserted into the center of the stopper mechanism. An electric valve is preferable, wherein the on-shaft guide hole is a hole on the inner circumference of the guide pipe, and the guided portion is the end portion of the rotor shaft.

Further, the bush is made of an elastic material, and an electric valve is characterized in that a load is applied to the contact surfaces of the inner circumference of the on-axis guide hole and the outer circumference of the guided portion in opposite directions in the radial direction. Is preferable.

The refrigeration cycle system of the present invention is a refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, and is characterized in that the electric valve is used as the expansion valve. do.

According to the electric valve and the refrigeration cycle system of the present invention, the guided portion is guided between the guided portion that moves in the axial direction integrally with the rotor shaft and the on-axis guide hole that holds the guided portion on the axis. Since a bush member that is lightly press-fitted into the portion and the shaft guide hole is provided, the load is applied inward in the radial direction with respect to the contact surface with the outer periphery of the guided portion by this bush member, and the shaft guide is also provided. A load is applied outward in the radial direction with respect to the contact surface with the inner circumference of the hole, that is, a load is applied to the outer circumference of the guided portion and the inner circumference of the on-axis guide hole in opposite directions in the radial direction with a bush member sandwiched between them. It hangs. As a result, the runout and inclination of the rotor shaft due to the clearance in the screw feed mechanism are suppressed, and the operability of the electric valve is stabilized.

It is a vertical sectional view of the electric valve of the 1st Embodiment of this invention. It is an enlarged vertical sectional view and plan sectional view of a main part in the vicinity of a bush member in the electric valve of 1st Embodiment of this invention. It is a figure explaining the operation of the bush member in the electric valve of the 1st Embodiment of this invention. It is a vertical sectional view of the electric valve of the 2nd Embodiment of this invention. It is a vertical sectional view of the electric valve of the 3rd Embodiment of this invention. It is a vertical sectional view of the electric valve of the 4th Embodiment of this invention. It is a vertical sectional view of the electric valve of the 5th Embodiment of this invention. It is a vertical sectional view of the electric valve of the 6th Embodiment of this invention. It is a figure which shows the refrigeration cycle system of embodiment of this invention.

Next, an embodiment of the electric valve of the present invention will be described with reference to the drawings. FIG. 1 is a vertical cross-sectional view of the electric valve of the first embodiment, FIG. 2 is an enlarged vertical cross-sectional view and a plan sectional view of a main part in the vicinity of the bush member in the electric valve of the first embodiment, and FIG. 2 (B) is a view. 2 (A) is a cross-sectional view taken along the line AA. Further, FIG. 3 is a diagram illustrating the operation of the bush member in the electric valve of the first embodiment. The concept of "upper and lower" in the following description corresponds to the upper and lower parts in the drawing of FIG.

The electric valve 100 has a valve housing 1 as a "valve body" formed of a metal member such as stainless steel or brass, and the valve housing 1 has a valve chamber 1A and a valve chamber 1A centered on the axis X. A cylindrical valve port 11 is formed, and a straight portion 12 is formed below the valve port 11. Further, a primary joint pipe 111 communicating with the valve chamber 1A from the side surface side is attached to the valve housing 1, and a secondary joint pipe 112 communicating with the straight portion 12 is attached to the lower end portion in the axis X direction. .. As a result, the valve chamber 1A and the secondary joint pipe 112 can be made conductive.

A valve guide member 13 is attached to the valve housing 1 by press fitting and caulking so as to be inserted into the valve chamber 1A from above, and a valve guide hole 13a is formed in the center of the valve guide member 13. .. Further, a rim 1a is formed at the upper end of the valve housing 1 so as to surround the outer peripheral portion of the upper end of the valve guide member 13, and the valve housing 1 has a cylindrical case so as to fit on the outer periphery of the rim 1a. 14 is assembled. The case 14 is fixed to the valve housing 1 by crimping the rim 1a and brazing the outer periphery of the bottom. Further, a support member 2 is attached to the upper end opening of the case 14.

The support member 2 has a substantially cylindrical holder portion 21 made of synthetic resin, and a stainless steel flange portion 22 integrally provided at an end portion of the holder portion 21 near the valve housing 1 by insert molding. The support member 2 is fixed to the case 14 by welding the flange portion 22 around the opening of the case 14. At the center of the holder portion 21 of the support member 2, a female screw portion 21a coaxial with the axis X of the valve port 11 and a screw hole thereof are formed, and a shaft guide hole 21b connected to the screw hole of the female screw portion 21a is formed. Further, a cylindrical slide hole 21c having a diameter larger than the inner circumference of the shaft guide hole 21b is formed. A cylindrical rod-shaped rotor shaft 3 is arranged in the screw hole of the female screw portion 21a and the shaft guide hole 21b. A male threaded portion 3a is formed on the outer circumference of the rotor shaft 3, and the male threaded portion 3a is screwed into the female threaded portion 21a of the holder portion 21.

The holder portion 21 has a guide male screw 211 formed of a spiral ridge on the outer periphery thereof, a lower end stopper 212 protruding radially from one lower end of the guide male screw 211, and an outer peripheral edge of the upper end portion of the guide male screw 211. The upper end stopper 213 is formed on the upper end stopper 213, respectively. A coil-shaped driven slider 214 is screwed onto the outer circumference of the guide male screw 211. The driven slider 214 is rotated in the same direction as the magnet rotor 62, which will be described later, rotates, and moves in the same direction (up and down) as the rotor shaft 3 following the guide male screw 211. Then, when the driven slider 214 comes into contact with the lower end stopper 212 or the upper end stopper 213, the upper and lower stop positions of the magnet rotor 62 are regulated.

A valve holder 4 is slidably fitted in the slide hole 21c of the support member 2 in the axis X direction, and the valve holder 4 holds a needle valve 5 as a "valve member" at the lower portion. The valve holder 4 includes a boss portion 42 fixed to the lower end of a cylindrical cylindrical portion 41, and a spring receiver 43, a compression coil spring 44, and a washer 45 inside the cylindrical portion 41. The needle valve 5 is formed of a metal member such as stainless steel or brass, and has a semi-elliptical needle portion 51 at the lower tip, a cylindrical rod-shaped rod portion 52 extending from the needle portion 51 in the axis X direction, and a rod portion. It has a flange portion 53 formed at the upper end of the 52. The needle valve 5 is inserted into the insertion hole 42a of the boss portion 42 of the valve holder 4, and the flange portion 53 is brought into contact with the boss portion 42 to be attached to the valve holder 4. Further, the rod portion 52 of the needle valve 5 is inserted into the valve guide hole 13a of the valve guide member 13. Further, the cylindrical portion 41 of the valve holder 4 is engaged with the rotor shaft 3. That is, a flange portion 3b is integrally formed at the lower end portion of the rotor shaft 3, the flange portion 3b sandwiches the washer 45 together with the upper end portion of the cylindrical portion 41, and the lower end portion of the rotor shaft 3 rotates at the upper end portion of the cylindrical portion 41. Engaged as possible. By this engagement, the valve holder 4 is supported in a state of being rotatably suspended by the rotor shaft 3.

A sealed case 61 is airtightly fixed to the upper end of the case 14 by welding or the like, and inside the sealed case 61, a magnet rotor 62 having a multi-pole magnetized outer peripheral portion and a rotor shaft 3 fixed to the center thereof. Is provided. Further, a stator coil 63 is arranged on the outer periphery of the sealed case 61, and the magnet rotor 62, the rotor shaft 3 and the stator coil 63 constitute a stepping motor 6. Then, when a pulse signal is given to the stator coil 63, the magnet rotor 61 is rotated according to the number of pulses, and the rotor shaft 3 is rotated.

With the above configuration, when the stepping motor 6 is driven, the magnet rotor 62 and the rotor shaft 3 rotate, and the rotor shaft 3 is driven by the screw feed mechanism between the male screw portion 3a of the rotor shaft 3 and the female screw portion 21a of the support member 2. Moves in the X direction of the axis. The needle valve 5 moves in the axis X direction together with the valve holder 4 due to the movement of the rotor shaft 3 in the axis X direction accompanying this rotation. Then, the needle valve 5 advances and retreats in the axis X direction with the needle portion 51 inserted into the valve port 11 to increase or decrease the opening area of the valve port 11. As a result, the flow rate of the fluid (coolant) flowing from the primary joint pipe 111 to the secondary joint pipe 112 or from the secondary joint pipe 112 to the primary joint pipe 111 is controlled.

The shaft guide hole 21b in the support member 2 is a cylindrical cavity and constitutes an "on-axis guide hole". Further, the rotor shaft 3 inserted through the shaft guide hole 21b constitutes a "guided portion" that moves in the axis X direction integrally with the male screw portion 3a and is held on the axis X by the shaft guide hole 21b. doing. Then, in the first embodiment, the bush member 71 is arranged in the constricted portion 31 formed in the lower part of the male screw portion 3a of the rotor shaft 3.

As shown in FIG. 2B, the bush member 71 is made of a C-shaped elastic material and is fitted into the constricted portion 31 of the rotor shaft 3. Then, the bush member 71 is lightly press-fitted into the shaft guide hole 21b of the support member 2, so that the outer circumference of the bush member 71 is brought into contact with the inner surface of the shaft guide hole 21b and the inside of the shaft guide hole 21b. The sliding resistance between the peripheral surface and the peripheral surface is kept small. Then, when the rotor shaft 3 moves in the valve closing direction (downward) from the state of FIG. 3A to the state of FIG. 3B, the male screw portion 3a urges the bush member 71 downward. , The bush member 71 applies a load to the inner peripheral surface of the shaft guide hole 21b in the outer diameter direction. At the same time, the bush member 71 applies a load in the inner diameter direction to the outer peripheral surface of the constricted portion 31 of the rotor shaft 3. As a result, the runout and inclination of the rotor shaft 3 due to the clearance in the "screw feed mechanism" including the male screw portion 3a and the female screw portion 21a are suppressed. Therefore, the operability of the electric valve is stable.

FIG. 4 is a vertical cross-sectional view of the electric valve of the second embodiment, and the same members and similar elements are designated by the same reference numerals in the following embodiments, and detailed description thereof will be omitted. The second embodiment of FIG. 4 differs from the first embodiment in that a cylindrical valve holder 4'is integrally formed with the rotor shaft 3 at the lower end of the rotor shaft 3, and a bush member is formed on the outer periphery of the valve holder 4'. 72 is arranged. That is, in this second embodiment, the slide hole 21c in the support member 2 is a cylindrical cavity and constitutes an "on-axis guide hole". Further, the valve holder 4'inserted through the slide hole 21c moves in the axis X direction integrally with the male screw portion 3a (and the rotor shaft 3), and is held on the axis X by the slide hole 21c. It constitutes the "part". Then, in this second embodiment, the bush member 72 is arranged in the constricted portion 4a'formed around the valve holder 4'. In this embodiment, the needle valve 5 is held in the valve holder 4'by the spring receiver 43'and the compression coil spring 44'.

In the second embodiment, the bush member 72 is lightly press-fitted into the slide hole 21c of the support member 2, so that the outer circumference of the bush member 72 is brought into contact with the inner surface of the slide hole 21c and the slide hole 21c is formed. The sliding resistance with the inner peripheral surface is kept small. Then, when the rotor shaft 3 moves in the valve closing direction (downward), the bush member 72 applies a load to the inner peripheral surface of the slide hole 21c in the outer diameter direction. At the same time, the bush member 72 applies a load in the inner diameter direction to the outer peripheral surface of the constricted portion 4a'formed in the valve holder 4'. As a result, the runout and inclination of the rotor shaft 3 due to the clearance in the "screw feed mechanism" including the male screw portion 3a and the female screw portion 21a are suppressed. Therefore, the operability of the electric valve is stable. The bush member 72 may also be made of a C-shaped elastic material as in the first embodiment.

FIG. 5 is a vertical cross-sectional view of the electric valve of the third embodiment. In the third embodiment, the bush member 73 is between the valve holder 4'and the slide hole 21c of the support member 2 as in the second embodiment. In the third embodiment, the bush member 73 is fitted into the constricted portion (recessed portion) 21c1 on the inner circumference of the slide hole 21c. The operation of this third embodiment is the same as that of the second embodiment. The slide hole 21c in the support member 2 constitutes a "on-axis guide hole" forming a cylindrical cavity, and the valve holder 4'is formed by the slide hole 21c. It constitutes a "guided portion" held on the axis X. Then, in the third embodiment, the valve guide 4'is lightly press-fitted into the bush member 73, so that the inner circumference of the bush member 73 comes into contact with the outer peripheral surface of the valve guide 4'and the valve guide The sliding resistance between the 4'and the outer peripheral surface is kept small. Then, when the rotor shaft 3 moves in the valve closing direction (downward), the bush member 73 applies a load to the outer peripheral surface of the valve guide 4'in the inner diameter direction. At the same time, the bush member 73 applies a load in the outer diameter direction to the inner peripheral surface of the constricted portion (recessed portion) 21c1 on the inner circumference of the slide hole 21c. As a result, the runout and inclination of the rotor shaft 3 due to the clearance in the "screw feed mechanism" including the male screw portion 3a and the female screw portion 21a are suppressed. Therefore, the operability of the electric valve is stable. The bush member 73 may also be made of a C-shaped elastic material as in the first embodiment.

FIG. 6 is a vertical cross-sectional view of the electric valve of the fourth embodiment, and the electric valve of the fourth embodiment includes a stepping motor 10 as an "electric motor", a valve housing 20 as a "valve body", and a valve. It includes a mechanism portion 30 and a sealed case 40 made of a non-magnetic material.

The sealed case 40 is formed in a substantially cylindrical shape with the upper end closed, and is airtightly fixed to the upper end of the valve housing 20 by welding or the like. The stepping motor 10 is arranged so as to face the rotor shaft 3 as in the above embodiment, the magnet rotor 10b rotatably arranged inside the sealed case 40, and the magnet rotor 10b on the outer periphery of the sealed case 40. It is composed of a stator coil 10c and other yokes, exterior members, etc. (not shown). The rotor shaft 3 is attached to the center of the magnet rotor 10b, and the rotor shaft 3 extends to the valve mechanism portion 30 side.

The valve housing 20 is made of stainless steel or the like and has a substantially cylindrical shape, and has a valve chamber 20R inside the valve housing 20. A primary joint pipe 111 conducting to the valve chamber 20R is connected to one side of the outer periphery of the valve housing 20, and a secondary joint pipe 112 is connected to a tubular portion extending downward from the lower end. A valve seat ring 20c having a valve port 20c1 is fitted on the valve chamber 20R side of the secondary joint pipe 112, and the secondary joint pipe 112 is conducted to the valve chamber 20R via the valve port 20c1.

The valve mechanism portion 30 includes a support member 30a, a valve holder 4', and a needle valve 30c as a "valve member". The support member 30a is made of, for example, a synthetic resin and is formed in a substantially cylindrical shape, and has a metal flange portion 30d integrally provided by insert molding on the outer periphery thereof, and the support member 30a is a valve via the flange portion 30d. It is fixed to the upper end of the housing 20. Further, at the center of the support member 30a, a female screw portion 30a1 coaxial with the axis X of the rotor shaft 3 and a screw hole thereof are formed, and a cylindrical "on-axis guide" having a diameter larger than the screw hole of the female screw portion 30a1 is formed. A slide hole 30e as a "hole" is formed.

The cylindrical valve holder 4'is formed integrally with the rotor shaft 3 at the lower end of the rotor shaft 3 as in the second and third embodiments. A bush member 74 is arranged between the valve holder 4'and the slide hole 30e of the support member 30a. In the fourth embodiment, the bush member 74 is fitted into the constricted portion (recessed portion) 30e1 on the inner circumference of the slide hole 30e. That is, in the fourth embodiment, the slide hole 30e in the support member 30 is a cylindrical cavity and constitutes an "on-axis guide hole". Further, the valve holder 4'inserted through the slide hole 30e moves in the axis X direction integrally with the male screw portion 3a (and the rotor shaft 3), and is held on the axis X by the slide hole 30e. It constitutes the "part". In the fourth embodiment, the needle valve 30c is held in the valve holder 4'by the spring receiver 43'and the compression coil spring 44'.

Then, in the fourth embodiment, the valve guide 4'is lightly press-fitted into the bush member 74, so that the inner circumference of the bush member 74 comes into contact with the outer peripheral surface of the valve guide 4', and the valve guide The sliding resistance between the 4'and the outer peripheral surface is kept small. Then, when the rotor shaft 3 moves in the valve closing direction (downward), the bush member 74 applies a load to the outer peripheral surface of the valve guide 4'in the inner diameter direction. At the same time, the bush member 74 applies a load in the outer radial direction to the inner peripheral surface of the constricted portion (recessed portion) 30e1 of the slide hole 30e. As a result, the runout and inclination of the rotor shaft 3 due to the clearance in the "screw feed mechanism" including the male screw portion 3a and the female screw portion 30a1 are suppressed. Therefore, the operability of the electric valve is stable.

In the fourth embodiment, the inner case 81 is fitted in the upper part of the closed case 40, and the bearing member 83 is fitted in the guide pipe 82 in the center of the inner case 81. The upper end portion (end portion) of the rotor shaft 3 is inserted into the inside of the bearing member 83, and the rotor shaft 3 is rotatably fitted inside the bearing member 83. Further, a rotation stopper mechanism is configured on the outer circumference of the guide tube 82 of the inner case 81. That is, the spiral guide wire body 84 is mounted on the outer periphery of the guide tube 82, and the movable stopper member 85 screwed into the spiral guide wire body 84 is provided. Then, as the magnet rotor 10b rotates, the movable stopper member 85 moves up and down while turning by screwing with the spiral guide wire body 83, and the movable stopper member 85 moves up and down while rotating, and the movable stopper member 85 moves to the lower end stopper 83a or the inner case of the spiral guide wire body 83. By abutting on the upper end stopper 81a of 81, the rotation range of the magnet rotor 10b, that is, the lower end position and the upper end position is regulated.

FIG. 7 is a vertical cross-sectional view of the electric valve of the fifth embodiment, and the difference from the fourth embodiment in the fifth embodiment is that the constricted portion 4a'formed around the valve holder 4'has a bush member. It is a point where 75 is arranged, and other configurations are the same as those of the fourth embodiment.

Then, in the fifth embodiment, the bush member 75 is lightly press-fitted into the slide hole 30e of the support member 30, so that the outer circumference of the bush member 75 is brought into contact with the inner surface of the slide hole 30e and the slide hole 30e. The sliding resistance between the 30e and the inner peripheral surface is kept small. Then, when the rotor shaft 3 moves in the valve closing direction (downward), the bush member 75 applies a load to the inner peripheral surface of the slide hole 30e in the outer diameter direction. At the same time, the bush member 75 applies a load in the inner diameter direction to the outer peripheral surface of the constricted portion 4a'formed in the valve holder 4'. As a result, the runout and inclination of the rotor shaft 3 due to the clearance in the "screw feed mechanism" including the male screw portion 3a and the female screw portion 30a1 are suppressed. Therefore, the operability of the electric valve is stable.

FIG. 8 is a vertical sectional view of the electric valve of the sixth embodiment, and the differences between the sixth embodiment and the fourth and fifth embodiments are the internal structure of the valve holder 4 and the valve holder 4. The connection structure with the rotor shaft 3 is the same as that of the first embodiment, and the bush member 76 is provided inside the rotation stopper mechanism. Other configurations are the same as those of the fourth embodiment and the fifth embodiment.

In the sixth embodiment, the upper end portion 3A of the rotor shaft 3 is arranged in the guide pipe 42 at the center of the inner case 41, and the bush member 76 is arranged on the outer periphery of the upper end portion 3A of the rotor shaft 3. ing. That is, in the sixth embodiment, the guide tube 42 in the center of the inner case 41 is a cylindrical cavity, and the inner circumference of the guide tube 42 constitutes an “on-axis guide hole”. Further, the constricted portion 3A at the upper end of the rotor shaft 3 inserted into the guide pipe 42 moves integrally with the male screw portion 3a (and the rotor shaft 3) in the axis X direction, and is moved on the axis X by the guide pipe 42. It constitutes a "guided portion" to be held.

Then, in the sixth embodiment, the bush member 76 (and the upper end portion 3A of the rotor shaft) is lightly press-fitted into the guide pipe 42, so that the outer periphery of the bush member 76 comes into contact with the inner peripheral surface of the guide pipe 42. At the same time, the sliding resistance between the guide tube 42 and the inner peripheral surface is kept small. Then, when the rotor shaft 3 moves in the valve closing direction (downward), the bush member 76 applies a load to the inner peripheral surface of the guide pipe 42 in the outer radial direction. At the same time, the bush member 76 applies a load in the inner diameter direction to the outer peripheral surface of the constricted portion 3A of the rotor shaft 3. As a result, the runout and inclination of the rotor shaft 3 due to the clearance in the "screw feed mechanism" including the male screw portion 3a and the female screw portion 30a1 are suppressed. Therefore, the operability of the electric valve is stable. The bush member 76 may be made of a C-shaped elastic material.

In each embodiment, the bush member is an example of a C-shaped elastic material, but the shape is not limited to this, and a load can be applied to the guided portion and the axial guide hole in opposite directions in the radial direction. Just do it.

FIG. 9 is a diagram showing a refrigeration cycle system of the embodiment. In the figure, reference numeral 100 is an electric valve of the embodiment of the present invention constituting an expansion valve, 200 is an outdoor heat exchanger mounted on an outdoor unit, 300 is an indoor heat exchanger mounted on an indoor unit, and 400 is a four-way valve. The flow path switching valve 500 constituting the above is a compressor. The electric valve 100, the outdoor heat exchanger 200, the indoor heat exchanger 300, the flow path switching valve 400, and the compressor 500 are each connected as shown by a conduit to form a heat pump type refrigeration cycle. The accumulator, pressure sensor, temperature sensor, etc. are not shown.

The flow path of the refrigeration cycle is switched between the flow path during the cooling operation and the flow path during the heating operation by the flow path switching valve 400. During the cooling operation, as shown by the solid arrow in the figure, the refrigerant compressed by the compressor 500 flows into the outdoor heat exchanger 200 from the flow path switching valve 400, and the outdoor heat exchanger 200 functions as a condenser. Then, the liquid refrigerant flowing out from the outdoor heat exchanger 200 flows into the indoor heat exchanger 300 via the electric valve 100, and the indoor heat exchanger 300 functions as an evaporator.

On the other hand, during the heating operation, as shown by the broken arrow in the figure, the refrigerant compressed by the compressor 500 is transferred from the flow path switching valve 400 to the indoor heat exchanger 300, the electric valve 100, the outdoor heat exchanger 200, and the flow path. The switching valve 400 and the compressor 500 are circulated in this order, the indoor heat exchanger 300 functions as a condenser, and the outdoor heat exchanger 200 functions as an evaporator. The electric valve 100 decompresses and expands the liquid refrigerant flowing from the outdoor heat exchanger 200 during the cooling operation and the liquid refrigerant flowing from the indoor heat exchanger 300 during the heating operation, and further controls the flow rate of the refrigerant.

Although the embodiments of the present invention have been described in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and the design changes, etc. within the range not deviating from the gist of the present invention, etc. Even if there is, it is included in the present invention.

1 Valve housing 1A Valve chamber 11 Valve port 12 Straight part 13 Valve guide member 13a Valve guide hole 14 Case 111 Primary joint pipe 112 Secondary joint pipe X Axis 2 Support member 21 Holder part 22 Flange part 21a Female thread part 21b Shaft guide hole 21c Slide hole 211 Guide male screw 212 Lower end stopper 213 Upper end stopper 214 Driven slider 3 Rotor shaft 3a Male screw part 4 Valve holder 1 Needle valve 41 Cylindrical part 42 Boss part 43 Spring receiver 44 Compressor coil spring 45 Washer 51 Needle part 52 Rod part 53 Flange part 61 Sealed case 62 Magnet rotor 63 Stator coil 2 Stepping motor 71 Bush member 72 Bush member 73 Bush member 74 Bush member 75 Bush member 76 Bush member 100 Electric valve 200 Outdoor heat exchanger 300 Indoor heat exchanger 400 Flow path switching valve 500 Compressor Machine

Claims (6)

A female screw portion formed on a support member on the valve body side and a male screw portion formed on the rotor shaft of the electric motor and arranged through the center of the female screw portion are provided, and the rotational movement of the magnet rotor of the electric motor is performed. In an electric valve in which the screw feed mechanism of the female thread portion and the male thread portion converts it into a linear motion in the axial direction of the rotor shaft, and the valve member connected to the rotor shaft controls the opening degree of the valve port.
A guided portion that moves integrally with the rotor shaft in the axial direction, an on-axis guide hole forming a cylindrical cavity that inserts the guided portion and holds the guided portion on the axis, and the guided portion. An electric valve provided between the shaft and the on-shaft guide hole and provided with a bush member which is lightly press-fitted into the guided portion and the on-shaft guide hole. The on-axis guide hole is a shaft guide hole formed in the support member coaxially with the female screw portion, and the guided portion is a constricted portion formed coaxially with the male screw portion of the rotor shaft. The electric valve according to claim 1. The on-axis guide hole is a slide hole formed in the support member coaxially with the female screw portion, and the guided portion is formed integrally with the rotor shaft and holds the valve member to hold the slide hole. The electric valve according to claim 1, wherein the valve holder is arranged inside. A stopper mechanism for restricting the rotation range of the magnet rotor is provided at an end of the rotor shaft opposite to the valve member, and a guide tube through which the end of the rotor shaft is inserted is provided in the center of the stopper mechanism. The electric valve according to claim 1, wherein the on-shaft guide hole is a hole on the inner circumference of the guide pipe, and the guided portion is the end portion of the rotor shaft. The bush is made of an elastic material, and a load is applied to the contact surfaces of the inner circumference of the on-axis guide hole and the outer circumference of the guided portion in opposite directions in the radial direction. The electric valve according to any one of 4. 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 5 is used as the expansion valve. A refrigeration cycle system characterized by that.

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