JP2002089731A - Motor-operated flow regulating valve and refrigerating cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a driving motor, to miniaturize the whole constitution, and to reduce an arranging space. SOLUTION: This motor-operated flow regulating valve 11 has an almost cylindrical pipe 12, a rotor 17, a speed reducer 22 and a moving mechanism 28 are arranged inside of this pipe 12, a valve element 32 is arranged in a tip part of a moving member 30 of the moving mechanism 28, a valve seat 33 having a hole 33b blocked up when fitting the valve element 32 is arranged inside one end part of the pipe 12, and a stator 34 is arranged outside the pipe 12. This constitution can set torque of the driving motor 37 small, and can be mininaturized.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electric flow control valve having a function of adjusting a flow rate of a fluid such as a substrate or a liquid, and a refrigeration cycle apparatus using the electric flow control valve.

[0002]

2. Description of the Related Art In a refrigerating cycle device incorporated in a refrigerator, an air conditioner, or the like, an expander provided between a condenser and an evaporator evaporates a high-temperature and high-pressure liquid refrigerant output from the condenser. The evaporator is configured to reduce the pressure so as to be easy to operate, and to secure the optimum flow rate of the refrigerant in the evaporator. The expander includes a capillary tube, fixed throttle means, variable throttle means, and the like. The fixed throttle means is constituted by, for example, a fixed orifice. The variable throttle means is constituted by, for example, an electromagnetic valve for duty ratio control, a manual expansion valve, a temperature expansion valve, an electric flow rate adjusting valve (electrically driven linear expansion valve), and the like.

Here, as an example of the electric flow regulating valve, there is an apparatus described in Japanese Patent Application Laid-Open No. 10-141536. As shown in FIG. 15, this device includes fluid inlets and outlets 1 and 2 which are orthogonal to each other, a valve body 3 which opens and closes a through hole 2a of one of the fluid inlets and outlets 2, and a stepping motor 4 which rotationally drives the valve body 3. It is configured. The valve element 3 is configured such that the opening amount of the through hole 2a, that is, the flow rate of the fluid can be adjusted according to the rotation amount.

[0004]

However, in the case of the above-mentioned conventional electric flow regulating valve, the stepping motor 4
In this configuration, the valve element 3 is directly connected to the rotor 4a, and the valve element 3 is rotationally driven. Therefore, the driving torque of the stepping motor 4 needs to be set large. For this reason, a large motor must be used as the stepping motor 4, and there is a disadvantage that the overall configuration of the electric flow regulating valve becomes large. Further, since the bearing of the rotor 4a of the stepping motor 4 is also used as a mechanism for rotatably supporting the valve element 3, there is a disadvantage that shaft loss increases.

Further, since the fluid inlets and outlets 1 and 2 are orthogonal to each other, there is a disadvantage that the space required for disposing the motorized flow regulating valve becomes large. Furthermore, since the opening amount of the valve element 3 is determined by the step angle of the stepping motor 4, in order to adjust the flow rate of the fluid with high accuracy,
It is necessary to reduce the step angle of the stepping motor 4. Therefore, when trying to adjust the flow rate with high accuracy,
The size of the stepping motor 4 must be increased, and there is a problem that the overall configuration becomes larger accordingly.

Accordingly, an object of the present invention is to reduce the size of the drive motor, to reduce the overall configuration, to reduce the installation space, and to reduce the size of the valve body and the valve seat. An object of the present invention is to provide an electric flow control valve and a refrigeration cycle device that can prevent biting.

[0007]

According to the present invention, there is provided an electric flow regulating valve comprising: a substantially cylindrical pipe made of a non-magnetic metal member;
A rotor provided with a rotating shaft and a permanent magnet rotatably provided inside the pipe and multipolarized in a radial direction, a bearing provided inside the pipe and rotatably supporting the rotating shaft, A speed reducer provided inside the pipe and connected to the rotating shaft, and a mover provided inside the pipe and movable in the axial direction, and the rotational force of the output shaft of the speed reducer is moved in the axial direction. A moving mechanism for transmitting the moving element to the moving element, a valve element provided at a tip end of the moving element, and a valve element provided inside one end of the pipe and closed when the valve element is fitted. It is characterized by comprising a valve seat having a hole, a stator provided outside the pipe, and fluid ports provided at both ends of the pipe.

[0008]

According to the above configuration, since the reduction gear is interposed between the rotor and the moving mechanism (that is, the valve body), the torque required for the drive motor can be reduced. Therefore, the drive motor, that is, the rotor and the stator can be miniaturized, so that the entire configuration of the electric flow control valve can be miniaturized. Further, since the fluid ports are provided at both ends of the pipe, the space for disposing the electric flow control valve can be reduced.

Further, in the case of the above configuration, it is preferable that the speed reducer is constituted by a planetary speed reducer. Further, the moving mechanism includes a screw portion provided on an output shaft of the reduction gear transmission, a screw hole provided so that the screw portion can be screwed into the movable member, and a movable member provided on the movable member. It is a good configuration to have a convex portion for preventing rotation and a receiving portion provided on the inner peripheral portion of the pipe and receiving the convex portion. Furthermore,
It is preferable that the valve body is formed in a conical shape.

[0011] A connecting screw portion is provided at one end or both ends of the outer peripheral portion of the pipe, and a speed reducer mounting member for mounting the speed reducer inside the pipe is provided. It is even more preferable that a through hole is provided so as to pass a fluid, and a bearing mounting member for mounting the bearing inside the pipe is provided, and a through hole is provided to pass the fluid through the bearing mounting member. .

It is preferable that the bearing is made of a composite material composed of a sliding component material having self-lubricating properties and a resin or metal. Further, it is a preferable configuration that the bearing is made of a composite material composed of amorphous carbon or spherical amorphous carbon and polyphenylene sulfide (PPS) or polyamideimide (PAI). Still further, the bearing may be made of a composite sintered material composed of binary tungsten and tungsten, or a composite sintered material composed of a copper-tin alloy, graphite, and binary tungsten, or nickel, graphite, and boron nitride. It is preferable to be composed of any of the composite sintered materials.

On the other hand, it is preferable that the speed reducer is provided with a clutch mechanism for preventing the torque of the rotary shaft from being transmitted to the output shaft when the load acting on the output shaft increases. . In this case, it is a good configuration that the reduction gear is constituted by a planetary reduction gear. Further, the moving mechanism is provided on a screw portion provided on an output shaft of the speed reduction device, a screw hole provided so that the screw portion can be screwed into the movable member, and provided on the movable member. It is preferable that the pipe comprises a rotation-preventing convex portion and a receiving portion provided on an inner peripheral portion of the pipe and receiving the convex portion.

Further, it is preferable that the clutch mechanism is realized by a configuration in which the driven side and the fixed side of the two internal gears are exchanged in the planetary reduction gear. In this case, one of the two internal gears of the planetary reduction gear is fixed to the output shaft, and the other is fixed to a reduction gear casing rotatably provided on an inner peripheral portion of the pipe. A is the frictional force between the casing and the inner peripheral portion of the pipe, B is the frictional force of the moving element of the moving mechanism,
It is preferable that when the loosening force of the screw portion of the moving mechanism is C and the tightening force of the screw portion of the moving mechanism is D, B <C <A <D is satisfied.

Further, an annular concave portion is provided on an inner peripheral portion of the pipe, and an annular convex portion which is slidably fitted in the concave portion is provided on an outer peripheral portion of the reduction gear casing, and an outer peripheral surface portion of the convex portion or At least one of the inner peripheral surface portions of the concave portion is provided with a solid lubricating film made of difluidized molybdenum, fluororesin, or the like, and biasing means for biasing the convex portion in the axial direction and pressing against the inner surface of the concave portion is provided. It may be configured as follows.

[0016] Further, a first monopolar magnetized magnet between the output shaft of the reduction gear and the moving mechanism is at least monopolar in the axial direction.
And a second magnetized in at least a single pole in the axial direction so as to have a different polarity from the magnetic material or the first permanent magnet.
Is preferably connected by a magnetic connection mechanism including a permanent magnet. In this case, a solid lubricating film made of mobilized molybdenum, fluororesin, or the like may be provided on the contact surface where the first permanent magnet and the magnetic body or the second permanent magnet contact.

The frictional force between the first permanent magnet and the magnetic material or the second permanent magnet is E, the frictional force of the moving element of the moving mechanism is B, It is preferable that when the loosening force of the screw portion is C and the tightening force of the screw portion of the moving mechanism is D, B <C <E <D is satisfied.

Still further, a third permanent magnet is provided at a radially outer end of the protrusion of the moving element of the moving mechanism, and a third permanent magnet is provided at an outer peripheral portion of the pipe at a position facing the third permanent magnet. It is a good configuration to provide a magnetic detection element. In this case, the shape of the convex portion is formed in a sector shape, and the circumferential end portion of the sector-shaped convex portion is configured to be received by two receiving portions, and the angle formed by these two receiving portions is defined by the angle. You may comprise larger than the fan angle of a convex part. It is also preferable that the third permanent magnet is formed in a sector shape and has a thin or thick wall thickness in the axial direction.

On the other hand, in a refrigeration cycle apparatus having a compressor, a condenser, an expander, and an evaporator in this order, and having a differential pressure regulating valve on an inlet side or an outlet side of the expander, the refrigeration cycle device may be configured as a differential pressure regulating valve. It is preferable that the electric flow control valve according to any one of Items 1 to 20 is used.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. First,
FIG. 1 is an overall longitudinal sectional view of the electric flow control valve 11 of the present embodiment. As shown in FIG. 1, the pipe 12 constituting the main body (outer shell) of the motorized flow control valve 11 is a substantially cylindrical pipe made of a non-magnetic metal member, for example, a member made of copper, aluminum, SUS304, or the like. . The upper end and the lower end of the pipe 12 are fluid ports 13 and 14.

At the upper and lower ends of the outer peripheral portion of the pipe 12, connecting screw portions 15 and 16 are formed. Through these threaded portions 15 and 16, the pipe 12
Are connected to other fluid pipes of the refrigeration cycle (for example, pipes through which a refrigerant flows).

A permanent magnet type rotor 17 is rotatably provided at a substantially intermediate portion inside the pipe 12. The rotor 17 includes a permanent magnet 18 that is magnetized to have multiple poles in a radial direction, and a rotating shaft 19 that is provided to penetrate the axis of the permanent magnet 18. The permanent magnet 18 and the rotating shaft 19 are fixed so as to rotate integrally by, for example, a method such as bonding, caulking, or welding.

The upper end of the rotating shaft 19 is rotatably supported by a bearing 20. The bearing 20 is formed of, for example, a self-lubricating sliding bearing.
As such a self-lubricating plain bearing, for example, a resin-based molding (construction) made of a composite material in which amorphous carbon or spherical amorphous carbon is mixed with a resin such as polyphenylene sulfide (PPS) or polyamide imide (PAI) is used. Bearings, composite sintered material consisting of two-way tungsten and tungsten, or
It is preferable to use a metal-based bearing or the like made of a composite sintered material composed of a copper-tin alloy, graphite, and disulfide tungsten, or a composite sintered material composed of nickel, graphite, and boron nitride.

The bearing 20 is mounted inside the pipe 12 via a bearing housing (bearing mounting member) 21. As shown in FIG. 5, the bearing housing 21 is an annular member, and the bearing 20 is fixed to a housing 21a provided on an inner peripheral portion thereof by, for example, bonding. The bearing housing 21 is a pipe 1
2 is fixed by, for example, an adhesive. And, as shown in FIG. 5, for example, four through holes 21b are formed in the bearing housing 21.

At the lower end of the rotary shaft 19 inside the pipe 12, a planetary reduction gear (reduction gear) 22 is provided. The lower end of the rotating shaft 19 is fitted and connected to the input portion of the planetary reduction gear 22 and is fixed by bonding or the like. That is, the rotation shaft 19 of the rotor 17 is the input shaft of the planetary reduction gear 22. Also, planetary reducer 2
The second output shaft 23 is rotatably supported by a bearing 24. The bearing 24 is mounted via a mounting member 26 inside a cylindrical case 25 of the planetary reduction gear 22. In this case, the bearing 24 and the mounting member 26 are fixed by, for example, adhesion. The attachment member 26 and the case 25 are fixed by, for example, an adhesive.

The bearing 24 is constituted by a bearing having the same structure as the bearing 20, that is, a sliding bearing having self-lubricating properties. In the case of this configuration, the rotating shaft 19 of the rotor 17 is rotatably supported by bearings 20 and 24. Further, the rotation shaft 19 and the output shaft 23 are arranged on the same axis (that is, the axis of the pipe 12).

The case 25 of the planetary reduction gear 22 is
It is mounted inside the pipe 12 via a reduction gear housing (reduction gear mounting member) 27. As shown in FIG. 6, the reduction gear housing 27 is an annular member, and the case 25 is fixed to the inner peripheral portion 27a thereof by, for example, bonding. The bearing housing 27 is fixed to the inside of the pipe 12 by, for example, bonding. Then, as shown in FIG.
For example, four through holes 27b are formed.

A moving mechanism 28 for converting the rotational force of the output shaft 23 of the planetary speed reducer 22 into a moving force in the axial direction is provided below the planetary speed reducer 22 inside the pipe 12. The moving mechanism 28 includes a screw member (screw portion) 29 attached to the tip of the output shaft 23 and a moving member (movable element) provided to be reciprocally movable in the axial direction of the pipe 12.
30. The screw member 29 is formed with a through hole 23a into which the output shaft 23 is fitted.
The output shaft 23 is fitted in the inside 3a and fixed by, for example, bonding or shrink fitting. On the outer periphery of the screw member 29,
A screw portion 29b is formed (see also FIG. 2).

The moving member 30 includes a cylindrical member 31.
And a valve body 32 attached to the lower end of the cylindrical member 31 in FIG. In this case, the valve element 32
Is provided at the distal end of the moving member 30. The screw member 2 is provided on the inner peripheral portion of the cylindrical member 31.
A screw portion 31a is formed in which the nine screw portions 29b mesh with each other, and the screw member 29 is screwed into the cylindrical member 31. As shown in FIG. 2, two protruding projections 3 are formed on the upper end of the outer periphery of the cylindrical member 31 in FIG.
1b and 31b are protruded in the lateral direction.

Here, as shown in FIGS. 1 to 3, the inner peripheral portion of the pipe 12 has the two convex portions 31b, 31b.
For example, stepped receiving portions 12a, 12a are formed to receive the light. In the case of this configuration, the cylindrical member 31 (moving member 3
0) is the receiving portion 12a of the pipe 12;
It is configured to be prevented from rotating by abutting on 12a. That is, the protrusions 31b, 31b are protrusions for preventing rotation.

Then, in this manner, the cylindrical member 31
With the (moving member 30) locked, the screw member 2
When the 9 (output shaft 23) is rotated, the cylindrical member 31 (moving member 30) is configured to move in the axial direction. In this case, the moving direction of the cylindrical member 31 (moving member 30) is determined by the rotating direction of the screw member 29 (output shaft 23). That is, when the screw member 29 is rotated in one direction, the cylindrical member 31 is moved downward in FIG. 1, and when the screw member 29 is rotated in the opposite direction, the cylindrical member 31 is moved upward in FIG. It has a configuration.

On the other hand, the valve element 32 includes a disk portion 32a fitted and fixed inside the cylindrical member 31, and a disk portion 32a.
a of FIG. 1A and a projection 32b protruding downward from the center of the lower surface in FIG. The protruding portion 32b is formed such that its tip has a substantially conical shape, for example.

A bottomed short cylindrical valve seat 33 is attached to the lower end of the pipe 12 in FIG. 1 by, for example, bonding or welding. As shown in FIGS. 1 and 4, the valve body 3 of the moving member 30 is provided on a bottom wall portion 33 a of the valve seat 33.
A hole 33b that is closed when the second protrusion 32b is fitted is formed. A tapered portion that guides when the convex portion 32b of the valve body 32 is fitted is formed at the upper end in FIG. 1 of the inner peripheral portion of the hole 33b.

A stator 34 is provided at a portion of the outer peripheral portion of the pipe 12 corresponding to the rotor 17. The stator 34 includes a stator core 35 attached to an outer peripheral portion of the pipe 12 and the stator core 3.
5 and a stator coil 36 wound around the stator coil 5. The stator 34 and the rotor 17 constitute a drive motor 37 for the electric flow control valve 11.
The drive motor 37 is a motor including a permanent magnet rotor 17, for example, a motor including a stepping motor or a DC brushless motor.

Next, the operation of the motorized flow control valve 11 having the above configuration will be described. When the stator coil 36 is energized to rotate the rotor 17, the rotation of the rotating shaft 19 is reduced by the planetary reducer 22, and the output shaft 23 rotates at low speed and high torque. Thereby, the screw member 29 of the moving mechanism 28 is rotated. At this time, the cylindrical member 31 of the moving member 30 is prevented from rotating, so that the cylindrical member 31 is moved in the axial direction.

As a result, when the valve element 32 attached to the cylindrical member 31 is moved in the axial direction, for example, when the valve element 32 is moved downward in FIG.
2b approaches the hole 33b of the valve seat 33, and the opening amount of the hole 33b gradually decreases. And the convex part 32 of the valve body 32
When b fits into the hole 33b of the valve seat 33, the hole 33b is closed. Conversely, when the valve body 32 is moved upward in FIG. 1, the conical convex portion 32b of the valve body 32 is moved in a direction away from the hole 33b of the valve seat 33, and the opening amount of the hole 33b gradually increases. The number of holes 33b eventually becomes completely open. In this case, the moving direction of the valve element 32, that is, the moving member 30 can be switched by switching the rotation direction of the rotor 17 forward and reverse.

The fluid pipes are connected so that, for example, the fluid flows into the pipe 12 from the fluid ports 13 of the fluid ports 13 and 14 at both ends of the pipe 12 and flows out from the fluid ports 14. I do. In this state,
As described above, when the valve body 32 is moved upward in FIG. 1 and the hole 33b of the valve seat 33 is opened, the fluid port 13
Flowing into the pipe 12 from the bearing housing 2
The fluid passes through the through hole 21b of the reduction gear housing 27, the through hole 27b of the reduction gear housing 27, the hole 33b of the valve seat 33, and flows out of the fluid port 14. The opening amount of the hole 33b of the valve seat 33 (that is, the moving position of the valve body 32)
Is controlled so that the flow rate of the fluid passing through the electric flow control valve 11 can be adjusted.
In this case, the movement position of the valve body 32 is controlled by the drive motor 3
7 by controlling the rotation direction and the number of rotations.

Now, an embodiment in which the above-mentioned electric flow regulating valve 11 is applied to, for example, a differential pressure regulating valve used in a refrigeration cycle apparatus incorporated in an air conditioner (air conditioner) will be briefly described with reference to FIG. Will be described. As shown in FIG. 7, the refrigeration cycle device 38 is configured by connecting a compressor 39, a condenser 40, a differential pressure regulating valve 41, an expander 42, and an evaporator 43 in order by a refrigerant pipe 44. Here, the electric flow control valve 11 having the above-described configuration is used as the differential pressure control valve 41. In the case of this configuration, a differential pressure regulating valve 41 is provided on the inlet side of the expander 42. The differential pressure regulating valve 41 may be provided on the outlet side of the expander 42.

The condenser 40 has an outdoor fan device 45.
It is configured to be cooled by the air blowing action. Furthermore, the cool air generated by the evaporator 43 is configured to be blown indoors by the blowing action of the indoor fan device 46.

According to the present embodiment having such a configuration, the planetary reduction gear 2 is disposed between the rotor 17 and the moving mechanism 28 of the valve body 32.
2, the torque required for the drive motor 37 can be reduced.
For this reason, since the drive motor 37, that is, the rotor 17 and the stator 34 can be downsized, the overall configuration of the electric flow control valve 11 can be downsized. Since the fluid inlets and outlets 13 and 14 are provided at both ends of the pipe 12, the space for disposing the electric flow control valve 11 can be reduced.

In the above embodiment, since the planetary reduction gear 22 is provided between the rotor 17 and the moving mechanism 28, the rotation shaft 19 of the rotor 17 and the output shaft 23 of the planetary reduction gear 22 are coaxial. , And the configuration of the entire apparatus can be made elongated (that is, small in diameter), so that the configuration built in the pipe 12 can be easily realized.

Further, in the above embodiment, the moving mechanism 28
Screw member 29 provided on output shaft 23 of planetary reduction gear 22
A cylindrical member 31 provided so that the screw member 29 can be screwed therein; a detent protrusion 31 b provided on the cylindrical member 31; and a receiving portion provided on an inner peripheral portion of the pipe 12. 12a. This makes it possible to easily change the amount of movement of the valve body 32 minutely. Also,
When the drive motor is cut off, the moving mechanism 28 and the planetary reducer 22
Thereby, the position of the valve body 32 can be reliably held.

In the above embodiment, since the convex portion 32b of the valve body 32 is formed in a substantially conical shape, the convex portion 32b is formed.
Even if the axis of b is misaligned with the axis of the hole 33b of the valve seat 33, it is corrected by self-alignment so that both axes coincide. For this reason, the component accuracy and the assembly accuracy of the moving mechanism 28 can be reduced, and the manufacturing cost can be reduced.

Further, in the above embodiment, the bearings 20, 24
Is composed of a composite material composed of a sliding component material having self-lubricating properties and a resin or metal (that is, a resin-based material or a metal-based material having self-lubricating properties), so that lubricating oil can be eliminated. The structure is simplified because a lubricating oil sealing mechanism is not required. In the above embodiment,
Since the fluid flowing through the electric flow regulating valve 11 can be configured to act as a bearing lubricant for the bearings 20 and 24,
The shaft loss can be further reduced.

FIG. 8 is a diagram showing a second embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals. In the second embodiment, a planetary speed reducer 51 having a clutch mechanism is provided instead of the planetary speed reducer 22 of the first embodiment. As shown in FIG. 8, the planetary speed reducer 51 includes a sun gear 52 provided at the lower end of the rotating shaft 19 as an input shaft, three planetary gears 53 meshing with the sun gear 52, and these planetary gears. First meshing with 53
And an internal gear 54 and a second internal gear 55.

The first internal gear 54 and the second internal gear 55 are
These gears have different numbers of teeth (ratio of the number of teeth). First internal gear 5
4 is fixed to the upper end of the inner peripheral portion of the case 25 of the planetary reduction gear 51 by bonding or the like. An annular member 61 is fixed to the outer periphery of the case 25 by bonding or the like. The annular member 61 is rotatably accommodated in an annular concave portion 56 provided on the inner peripheral portion of the pipe 12. The case 25 and the annular member 61 constitute a reduction gear casing 62, and the annular member 61 constitutes an annular convex portion. The annular member 61 has a plurality of through holes 61.
a (corresponding to the through hole 27a of the first embodiment).

In this case, between the outer peripheral surface of the annular member 61 and the inner peripheral surface of the concave portion 56, an appropriate magnitude of frictional force as described later is generated. The concave portion 56 is formed by disposing a cylindrical member 57 on the inner peripheral portion of the pipe 12. A semi-cylindrical member 58 is provided on the inner peripheral portion of the cylindrical member 57 in order to form the stepped receiving portions 12a, 12a.

At the lower end of the inner periphery of the case 25,
A bearing 24 is fixed via a mounting member 26, and the output shaft 23 is rotatably supported by the bearing 24.
The bearing 24 is fixed to the mounting member 26 by bonding or the like.
The attachment member 26 is fixed to the case 25 by bonding or the like.

On the other hand, the second internal gear 55 is
And is fixed to the upper end portion of the output shaft 23 via the. In this case, the second internal gear 55 is fixed to the output joint 59 by adhesion or the like, and the output joint 59 is fixed to the upper end of the output shaft 23 by adhesion or the like. The planetary reduction gears 5 other than those described above
The configuration of No. 1 is the same as that of the planetary reduction gear 22 of the first embodiment. In addition, the configuration of the motorized flow control valve 11 of the second embodiment other than that described above has the same configuration as the motorized flow control valve 11 of the first embodiment.

Next, the operation of the motorized flow regulating valve 11 of the second embodiment will be described. When the rotor 17 is rotated by energizing the stator coil 36 of the drive motor 37, the rotation of the rotating shaft 19 is reduced by the planetary reducer 51, and the output shaft 23 rotates at low speed and high torque. Thereby, the screw member 29 of the moving mechanism 28 is rotated. At this time, the cylindrical member 31 of the moving member 30 is prevented from rotating, so that the cylindrical member 31 is moved in the axial direction.

Thus, when the valve element 32 attached to the cylindrical member 31 is moved in the axial direction, for example, when the valve element 32 is moved downward in FIG.
2b approaches the hole 33b of the valve seat 33, and the opening amount of the hole 33b gradually decreases. And the convex part 32 of the valve body 32
When b fits into the hole 33b of the valve seat 33, the hole 33b is closed. Conversely, when the valve element 32 is moved upward in FIG. 8, the conical convex portion 32b of the valve element 32 is moved in a direction away from the hole 33b of the valve seat 33, and the opening amount of the hole 33b gradually increases. The number of holes 33b eventually becomes completely open. In this case, the moving direction of the valve element 32, that is, the moving member 30 can be switched by switching the rotation direction of the rotor 17 forward and reverse.

In the case of the above configuration, by controlling the opening amount of the hole 33b of the valve seat 33, that is, the moving position of the valve element 32, the flow rate of the fluid passing through the electric flow rate adjusting valve 11 can be adjusted. Is configured. In this case, the valve element 32
Is controlled by controlling the rotation direction and the number of rotations of the drive motor 37.

As described above, when the output shaft 23 of the planetary reduction gear 51 is rotating in the forward or reverse direction, the annular member 61, the case 25, and the first internal gear 54 Stopped without rotation. These annular members 61
The force for stopping the operation is a frictional force between the outer peripheral surface of the annular member 61 and the inner peripheral surface of the concave portion 56 of the pipe 12.

When the valve body 32 is moved downward in FIG. 8 and the projection 32b of the valve body 32 completely closes the hole 33b of the valve seat 33, the drive motor 37 ( If the energization control that keeps rotating 17) is performed, the valve body 32 cannot move further downward. In such a case, a tightening force is generated on the screw member 29 of the moving mechanism 28. When the tightening force of the screw member 29 becomes larger than the frictional force between the outer peripheral surface of the annular member 61 and the inner peripheral surface of the concave portion 56 of the pipe 12, the output shaft 2
3 and the second internal gear 55 are fixed, and the first internal gear 54
And the annular member 61 is configured to rotate. That is, in the planetary reduction gear 51, when the load acting on the output shaft 23 increases, the rotational force of the rotation shaft 19 is
3 is switched so as not to be transmitted.

When the rotor 17 is rotated in the opposite direction in this state, the tightening force of the screw member 29 of the moving mechanism 28 is reduced. The frictional force between the outer peripheral surface and the inner peripheral surface of the concave portion 56 of the pipe 12 is larger.
As a result, the annular member 61 and the first internal gear 54 are fixed, and the output shaft 23 and the second internal gear 55 rotate. Thereby, the valve element 32 is moved upward in FIG.
The opening amount of the hole 33b increases, and the hole 33b is completely opened.

After the hole 33b is completely opened,
When the energization control for keeping the rotor 17 rotating is performed, the screw member 29 of the moving mechanism 28
When it comes into contact with the end face of 1a, a tightening force is generated in the screw member 29. Therefore, also in this case, similarly to the above-described case, when the tightening force of the screw member 29 becomes larger than the frictional force between the outer peripheral surface of the annular member 61 and the inner peripheral surface of the concave portion 56 of the pipe 12. The output shaft 23 and the second internal gear 55 are fixed, and the first internal gear 54 and the annular member 61 are switched so as to rotate.

In the above configuration, when the load acting on the output shaft 23 is small, the torque of the rotating shaft 19 is transmitted to the output shaft 23, and when the load acting on the output shaft 23 is large, The clutch mechanism for preventing transmission of the torque to the output shaft 23 is built in the planetary reduction gear 51. The clutch mechanism is realized by a configuration in which the driven side and the fixed side of the two internal gears 54 and 55 in the planetary reduction gear 51 are switched. The planetary gear mechanism 51 having such a clutch mechanism is provided.
Can be configured with a planetary gear mechanism commonly referred to as a 3K type mysterious planetary gear mechanism (refer to “Actuator technology for micro robots” written by Koichi Suzumori, Kohei Hori, Toyomi Miyagawa, Akihiro Koga). It is.

In the case of the second embodiment, one of the two internal gears 54 and 55 of the planetary reduction gear 51 is fixed to the output shaft 23, and the other is rotatable around the inner peripheral portion of the pipe 12. The moving mechanism 28 is fixed to the annular member 61 provided, and the frictional force between the annular member 61 and the inner peripheral portion of the pipe 12 is A.
B is the frictional force of the moving member 30 and C is the loosening force of the screw member 29 of the moving mechanism 28.
When the tightening force of No. 9 is D, B <C <A <D holds.

According to the second embodiment having such a structure,
The same operation and effect as in the first embodiment can be obtained. In particular, in the case of the second embodiment, when the load acting on the output shaft 23 is small, the rotational force of the rotating shaft 19 is transmitted to the output shaft 23, and when the load acting on the output shaft 23 increases,
Since the planetary reduction gear 51 has a built-in clutch mechanism for preventing the torque of the rotating shaft 19 from being transmitted to the output shaft 23, it is ensured that the convex portion 32 b of the valve body 32 bites into the hole 33 b of the valve seat 33. Can be prevented. Further, it is possible to prevent the drive motor 37 incorporated in the electric flow control valve 11 from being locked.

In the second embodiment, the clutch mechanism built in the planetary reduction gear 51 is provided with two internal gears 5.
The clutch mechanism can be easily realized with a simple structure because the structure is realized by exchanging the driven side and the fixed side of 4, 55.

By the way, as a conventional structure provided with a mechanism for preventing biting of a valve, there are structures described in JP-A-10-169821, JP-B-3-51574 and JP-B-3-4866. In these configurations, a stopper is provided, and the rotation of the motor is forcibly stopped by the stopper, thereby preventing biting of the valve.

However, in the case of such a conventional configuration, the strength of the stopper is considerably required, so that there is a problem that the configuration of the apparatus becomes large. If the torque of the motor is reduced, the strength of the stopper is not so required. However, if the torque of the motor is reduced, a problem occurs that the valve cannot be fully closed or fully opened. In addition, since a considerable mechanical shock is generated at the stopper portion, there is a problem that large abnormal noise, vibration, and the like are generated, and the life of the device is shortened.

On the other hand, according to the second embodiment, when the load acting on the output shaft 23 increases, the clutch mechanism for preventing the torque of the rotating shaft 19 from being transmitted to the output shaft 23 is provided. Since it is built in the planetary reduction gear 51, it is not necessary to use the above stopper, and the configuration can be downsized, and generation of loud noise and vibration can be prevented.
The life of the device can be extended.

FIG. 9 is a diagram showing a third embodiment of the present invention. The same parts as those in the second embodiment are denoted by the same reference numerals. In the third embodiment, as shown in FIG. 9, an annular concave portion 56 provided on the inner peripheral portion of the pipe 12 is provided.
And a solid lubricating coating made of, for example, molybdenum difluoride or a fluororesin, is provided on the inner peripheral surface of the gearbox and the outer peripheral surface of the annular member 61 provided on the outer peripheral portion of the reduction gear casing 62. Note that the solid lubricating film may be provided on only one of the inner peripheral surface of the concave portion 56 and the outer peripheral surface of the annular member 61.

A coil spring 64 as a biasing means is disposed between the upper inner surface of the recess 56 in FIG. 9 and the upper outer surface of the annular member 61 in FIG. .
Due to the spring force of the coil spring 64, the annular member 61 is urged to move downward in FIG. 9 and is pressed against the inner surface of the concave portion 56 on the lower side in FIG. Note that a leaf spring may be used instead of the coil spring 64.

In the case of the above configuration, the magnitude of the frictional force between the annular member 61 of the reduction gear casing 62 and the concave portion 56 of the pipe 12 can be adjusted by adjusting the spring force of the coil spring 64. Have been.

The configuration of the third embodiment other than the above is the same as the configuration of the second embodiment. Therefore, the same operation and effect as in the second embodiment can be obtained in the third embodiment. In particular, according to the third embodiment, the annular member 61 of the reduction gear casing 62 and the pipe 1
Since the magnitude of the frictional force between the second concave portion 56 and the second concave portion 56 can be adjusted, it is possible to more reliably prevent the convex portion 32b of the valve body 32 from biting into the hole 33b of the valve seat 33.

FIG. 10 is a diagram showing a fourth embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals. In the fourth embodiment, the reduction gear housing 27 of the planetary reduction gear 22 is fixed to the inner peripheral surface of the pipe 12 by bonding or the like, and the planetary reduction gear 22 has a clutch mechanism (see the second embodiment). ) Are not built-in.

In the fourth embodiment, as shown in FIG. 10, a disk-shaped first permanent magnet 65 is fixed to the lower end of the output shaft 23 of the planetary reduction gear 22 by bonding or the like. The end face of the first permanent magnet 65 is monopolar (that is, monopolar in the axial direction). Then, the moving mechanism 28
A disk-shaped second permanent magnet 66 is fixed to the upper end of the screw member 29 by bonding or the like. The second permanent magnet 66 is monopolar (that is, monopolar in the axial direction) so that its end face is different from the first permanent magnet 65.

First permanent magnet 65 and second permanent magnet 66
Are connected by magnetic attraction, and are configured so that the rotational force of the output shaft 23 is transmitted to the screw member 29 (moving mechanism 28) via the permanent magnets 65 and 66. That is,
The first permanent magnet 65 and the second permanent magnet 66 constitute a magnetic coupling mechanism 67.

The lower surface of the first permanent magnet 65 and the second
On the upper surface of the permanent magnet 66, a solid lubricating film made of di-mobilized molybdenum, fluororesin, or the like is provided. That is,
The solid lubricating coating is provided on the contact surface where the two permanent magnets 65 and 66 come into contact. The first permanent magnet 6
The solid lubricating film may be provided only on one of the lower surface of the fifth permanent magnet 66 and the upper surface of the second permanent magnet 66.

In the case of the fourth embodiment, when the valve element 32 completely closes or completely opens the hole 33b of the valve seat 33, the energization control continues to rotate the rotor 17 thereafter. Is performed, the screw member 2 of the moving mechanism 28
9 generates a tightening force. The tightening force of the screw member 29 is applied to the two permanent magnets 65 of the magnetic coupling mechanism 67,
If the friction between the two permanent magnets 65 and 66 becomes larger than the frictional force between the two based on the magnetic attraction force of 66, a slip occurs between the two permanent magnets 65 and 66, and the rotational force of the output shaft 23 of the planetary reduction gear 22 is reduced by the screw of the moving mechanism 28. The transmission is not transmitted to the member 29.

In the case of the fourth embodiment, the frictional force between the first permanent magnet 65 and the second permanent magnet 66 is E,
Let B be the frictional force of the moving member 30 of the moving mechanism 28 and C be the loosening force of the screw member 29 of the moving mechanism 28.
When the tightening force of the screw member 29 is D, B <C <E <D is satisfied.

The configuration of the fourth embodiment other than that described above is the same as the configuration of the first embodiment. Therefore, the same operation and effect as in the first embodiment can be obtained in the fourth embodiment. In particular, according to the fourth embodiment, the tightening force generated in the screw member 29 of the moving mechanism 28 is smaller than the frictional force between the two permanent magnets 65 and 66 of the magnetic coupling mechanism 67 based on the magnetic attractive force. When the rotation speed of the output shaft 23 of the planetary reduction gear 22 is increased, the protrusion 32 b of the valve body 32 is inserted into the hole 33 b of the valve seat 33. Biting can be reliably prevented.

In the fourth embodiment, one of the two permanent magnets 65 and 66 of the magnetic coupling mechanism 67 may be made of a disk-shaped magnetic material. With this configuration, the same operation and effect as those of the fourth embodiment can be obtained. When one is made of a disk-shaped magnetic material, the other permanent magnet may be multipolar magnetized. Furthermore,
In the fourth embodiment, the magnetic coupling mechanism 67 is configured to be incorporated in the electric flow control valve 11 of the first embodiment.
Instead of this, the magnetic coupling mechanism 67 may be configured to be incorporated in the motorized flow regulating valve (provided with the planetary reduction gear 51 having the clutch mechanism) 11 of the second embodiment.

FIG. 11 is a diagram showing a fifth embodiment of the present invention. The same parts as those of the fourth embodiment are denoted by the same reference numerals. In the fifth embodiment, as shown in FIG. 11, the outer periphery of the cylindrical member 31 of the moving mechanism 28 is
Instead of the protrusion 31b, a protrusion 69 extended in the axial direction was formed. Then, a third permanent magnet 70 was provided at a radially outer end of the right convex portion 69 in FIG.

When the cylindrical member 31 of the moving mechanism 28 moves to a position where the valve is fully closed, the third permanent magnet 70 of the convex portion 69 on the outer peripheral portion of the pipe 12 is moved to a position facing the third permanent magnet 70. , A first magnetic detection element 71 composed of a Hall element and the like. Then, the cylindrical member 3 of the moving mechanism 28
When the first permanent magnet 7 moves to a position where the valve 1 is fully opened, the third permanent magnet 7
A second magnetic detection element 72 composed of a Hall element or the like is provided at a position where 0 faces.

The configuration of the fifth embodiment other than that described above is the same as the configuration of the fourth embodiment. Therefore, in the fifth embodiment, the same operation and effect as those of the fourth embodiment can be obtained. In particular, according to the fifth embodiment, the fact that the valve has been fully closed can be determined by the first magnetic detection element 71 detecting the magnetic flux of the third permanent magnet 70 of the projection 69. Further, it can be determined that the valve has been fully opened by the second magnetic detection element 72 detecting the magnetic flux of the third permanent magnet 70 of the projection 69. Thus, the stop control of the drive motor 37 when the valve is fully opened / closed can be easily executed.

FIG. 12 is a diagram showing a sixth embodiment of the present invention. The same parts as in the fifth embodiment are denoted by the same reference numerals. In the sixth embodiment, as shown in FIG. 12, the outer peripheral portion of the cylindrical member 31 of the moving mechanism 28
Instead of the convex portion 69, a fan-shaped convex portion 73 was formed. The circumferential end of the fan-shaped projection 73 is connected to the pipe 12
The two receiving portions 74a and 74b provided on the inner peripheral portion of the device are configured to receive the signals. Furthermore, these two receiving parts 74a, 7
The angle formed by 4b is larger than the fan angle of the fan-shaped convex portion 73.

Further, a third permanent magnet 75 is provided on the outer periphery of the projection 73. Further, the cylindrical member 31 of the moving mechanism 28
Moves to the position where the valve is fully closed, the pipe 1
The third permanent magnet 75 of the convex portion 73 on the outer peripheral portion of the second permanent magnet 75
A first magnetic detection element 76 composed of a Hall element or the like is provided at a position where the right end in FIG. Then, when the cylindrical member 31 of the moving mechanism 28 moves to a position where the valve is fully opened, the left end in FIG. 5 of the third permanent magnet 75 of the convex portion 73 on the outer peripheral portion of the pipe 12 approaches. A second magnetic detecting element 77 composed of a Hall element or the like was provided at a position facing the second magnetic detecting element 77.

The configuration of the sixth embodiment other than that described above is the same as the configuration of the fifth embodiment. Therefore, also in the sixth embodiment, the same operation and effect as those of the fifth embodiment can be obtained. In particular, according to the sixth embodiment, the rotational direction of the convex portion 73, that is, the moving direction of the moving mechanism 28 can be detected by the two magnetic detecting elements 76 and 77.

FIG. 13 is a diagram showing a seventh embodiment of the present invention. The same parts as those in the sixth embodiment are denoted by the same reference numerals. In the seventh embodiment, as shown in FIG. 13, a third permanent magnet 78 having a two-pole magnet in the circumferential direction was used. The third permanent magnet 78 is formed so as to be tapered in the axial direction so that the thickness of the third permanent magnet 78 is gradually reduced or increased in the axial direction. Further, one magnetic detecting element 79 is arranged at substantially the center of the angle (sector angle) formed by the two receiving portions 74a and 74b on the outer peripheral portion of the pipe 12.

In the case of this configuration, when the cylindrical member 31 of the moving mechanism 28 moves in the valve closing direction, the N pole of the third permanent magnet 78 faces the magnetic detecting element 79 and the third permanent magnet 78 The gap between the magnetic detection element 79 and the magnetic detection element 79 is narrowed, and the output level of the detection signal of the magnetic detection element 79 is increased. When the cylindrical member 31 of the moving mechanism 28 moves in the valve opening direction, the third permanent magnet 7
8, the gap between the third permanent magnet 78 and the magnetic detection element 79 is widened, and the output level of the detection signal of the magnetic detection element 79 is reduced. Have been.

Thus, based on the polarity of the detection signal of the magnetic detection element 79 and the magnitude of the output level, the fully closed position and fully opened position of the valve, the opening degree of the valve, and the like can be detected. As a result, the motor stop control when the valve is fully opened / closed can be easily executed, and the flow rate control according to the opening degree of the valve can be easily executed.

The configuration of the seventh embodiment other than the above is the same as the configuration of the sixth embodiment. Therefore, also in the seventh embodiment, the same operation and effect as in the sixth embodiment can be obtained. In particular, according to the seventh embodiment, the number of magnetic sensing elements can be reduced.

FIG. 14 is a diagram showing an eighth embodiment of the present invention. In the eighth embodiment, the air conditioner 80 capable of the cooling operation and the heating operation is provided with the first to seventh air conditioners.
Was applied. A refrigeration cycle device 81 as shown in FIG. 14 is incorporated in the air conditioner 80 of the eighth embodiment.

The refrigeration cycle device 81 is provided with a compressor 8
2, a four-way valve 83, an outdoor heat exchanger 85 having an outdoor fan 84, an electronic control valve 86 as a throttle device, and an indoor fan 87
Are connected by a refrigerant pipe 89 as shown in the figure. Here, the above-described first to seventh electric flow rate adjusting valves 11 are used as the electronic control valve 86.

In this configuration, when the refrigerant is circulated by the switching operation of the four-way valve 83 as shown by the solid arrow in FIG. 14, the cooling operation is executed. On the other hand, when the refrigerant is circulated by the switching operation of the four-way valve 83, as indicated by the dashed arrow in FIG. 14, the heating operation is performed. By controlling the opening of the electronic control valve 86, the flow rate of the refrigerant can be adjusted.

In each of the above embodiments, the speed reducer is constituted by the planetary speed reducer 22. However, the present invention is not limited to this, and a speed reducer constituted by a gear such as a spur gear or a helical gear may be used. You may. Further, in the above embodiment, the convex portion 32b of the valve body 32 is formed in a conical shape, but may be formed in various shapes such as a cylindrical shape or a spherical shape instead.

Further, in each of the above embodiments, the connecting screw portions 15 and 16 are provided at both ends of the outer peripheral portion of the pipe 12.
The configuration is not limited to this, and the configuration may be such that the shape of the connecting portion is appropriately changed according to the shape of the device or device to be connected. Further, in the above embodiment, the bearings 20 and 24 are made of a resin-based material or a metal-based material having self-lubricating properties, but may be made of a ball bearing or a sintered oil-impregnated bearing instead.

[0091]

As is apparent from the above description, the present invention provides a substantially cylindrical pipe made of a non-magnetic metal member,
A rotor provided with a rotating shaft and a permanent magnet rotatably provided inside the pipe and multipolarized in a radial direction, a bearing provided inside the pipe and rotatably supporting the rotating shaft, A speed reducer provided inside the pipe and connected to the rotating shaft, and a mover provided inside the pipe and movable in the axial direction, and the rotational force of the output shaft of the speed reducer is moved in the axial direction. A moving mechanism for transmitting the moving element to the moving element, a valve element provided at a tip end of the moving element, and a valve element provided inside one end of the pipe and closed when the valve element is fitted. A valve seat having a hole, a stator provided outside the pipe, and a fluid port provided at both ends of the pipe are configured to include:
The drive motor can be reduced in size, so that the overall configuration can be reduced in size, and furthermore, there is an excellent effect that the installation space can be reduced.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of an electric flow regulating valve showing a first embodiment of the present invention.

FIG. 2 is a cutaway perspective view showing a moving mechanism and a peripheral portion thereof.

FIG. 3 is a cutaway perspective view showing a valve body and a peripheral portion thereof.

FIG. 4 is a perspective view showing a valve body and a valve seat.

FIG. 5 is a perspective view of a bearing housing.

FIG. 6 is a perspective view of a reduction gear housing.

FIG. 7 is a block diagram of a refrigeration cycle device.

FIG. 8 is a cutaway perspective view of an electric flow control valve according to a second embodiment of the present invention.

FIG. 9 is a partially cutaway perspective view of an electric flow control valve showing a third embodiment of the present invention.

FIG. 10 is a partial perspective view of an electric flow control valve according to a fourth embodiment of the present invention.

FIG. 11 is a partially cutaway perspective view of an electric flow control valve according to a fifth embodiment of the present invention.

FIG. 12 is a partially cutaway perspective view of an electric flow control valve according to a sixth embodiment of the present invention.

FIG. 13 is a partially cutaway perspective view of an electric flow control valve according to a seventh embodiment of the present invention.

FIG. 14 is a block diagram of a refrigeration cycle apparatus showing an eighth embodiment of the present invention.

FIG. 15 is a diagram corresponding to FIG. 1 showing a conventional configuration.

[Explanation of symbols]

11 is an electric flow regulating valve, 12 is a pipe, 12a is a receiving portion, 13 and 14 are fluid ports, 17 is a rotor, 18 is a permanent magnet, 19 is a rotating shaft, 20 is a bearing, and 21 is a bearing housing (bearing mounting member). , 21b are through holes, 22 is a planetary reduction gear (reduction gear), 23 is an output shaft, 24 is a bearing, 26 is a mounting member, 27 is a reduction gear housing (reduction gear mounting member), 28 is a moving mechanism, and 29 is a screw. Member (screw part), 3
0 is a moving member (moving element), 31 is a cylindrical member, 31b is a convex portion, 32 is a valve body, 33 is a valve seat, 33b is a hole, 34 is a stator, 37 is a drive motor, 38 is a refrigeration cycle device,
39 is a compressor, 40 is a condenser, 41 is a differential pressure regulating valve (electric flow regulating valve), 42 is an expander, 43 is an evaporator, 44 is a refrigerant pipe, 51 is a planetary reducer, 52 is a sun gear, 53 Is a planetary gear, 54 is a first internal gear, 55 is a second internal gear,
56 is a concave portion, 57 is a cylindrical member, 58 is a semi-cylindrical member, 59
Is an output joint, 60 is a feed screw portion, 61 is an annular member (convex portion), 62 is a reduction gear casing, 63 is a solid lubricating film, 64 is a coil spring (biasing means), 65 is a first permanent magnet, 66 Is a second permanent magnet, 67 is a magnetic coupling mechanism, 6
8 is a solid lubricating film, 69 is a convex portion, 70 is a third permanent magnet, 71 is a first magnetic detecting element, 72 is a second magnetic detecting element, 73 is a convex portion, 74a and 74b are receiving portions, 75 Is the third permanent magnet, 76 is the first magnetic detecting element, 77 is the second permanent magnet.
, 78 is a third permanent magnet, 79 is a magnetic detection element, 80 is an air conditioner, 81 is a refrigeration cycle device, 82 is a compressor, 83 is a four-way valve, 86 is an electronic control valve (electric flow rate adjustment). Valve).

Claims (15)

[Claims] 1. A substantially cylindrical pipe made of a non-magnetic metal member, a rotor rotatably provided inside the pipe, and having a permanent magnet and a rotating shaft which are magnetized to have multiple poles in a radial direction, A bearing provided inside the pipe and rotatably supporting the rotating shaft; a speed reducer provided inside the pipe and connected to the rotating shaft; provided inside the pipe and axially provided A moving mechanism that has a movable mover and converts the rotational force of the output shaft of the reduction gear into an axial movement force and transmits it to the mover; and a valve body provided at a tip end of the mover. A valve seat provided inside one end of the pipe and having a hole that is closed when the valve body is fitted; a stator provided outside the pipe; provided at both ends of the pipe Fluid inlet and outlet Electric flow control valve. 2. The motor-operated flow control valve according to claim 1, wherein the speed reducer comprises a planetary speed reducer. 3. The moving mechanism includes: a screw portion provided on an output shaft of the speed reducer; a screw hole provided so that the screw portion can be screwed into the movable member; The motorized flow control valve according to claim 1, further comprising: a rotation preventing protrusion provided on the inner surface of the pipe, and a receiving portion provided on an inner peripheral portion of the pipe to receive the protrusion. 4. The electric flow control valve according to claim 1, wherein the valve body is formed in a conical shape. 5. A connection screw portion provided at one or both ends of an outer peripheral portion of the pipe, a reduction gear mounting member for mounting the reduction gear inside the pipe,
A through hole provided to allow the fluid to pass through the reduction gear mounting member; a bearing mounting member for mounting the bearing inside the pipe; and a through hole provided to allow the fluid to pass through the bearing mounting member. The electric flow regulating valve according to any one of claims 1 to 4, further comprising: 6. The electric motor according to claim 1, wherein the bearing is made of a composite material made of a sliding component material having self-lubricating properties and a resin or a metal. Flow control valve. 7. The speed reducer is provided with a clutch mechanism for preventing the torque of the rotating shaft from being transmitted to the output shaft when the load acting on the output shaft increases. The electric flow regulating valve according to claim 1, wherein 8. The electric flow regulating valve according to claim 7, wherein the speed reducer is constituted by a planetary speed reducer. 9. The moving mechanism includes: a screw portion provided on an output shaft of the speed reducer; a screw hole provided so that the screw portion can be screwed into the movable member; The motorized flow control valve according to claim 7, further comprising: a protrusion provided for preventing rotation provided; and a receiving portion provided on an inner peripheral portion of the pipe and receiving the protrusion. 10. The clutch mechanism according to claim 8, wherein the planetary reduction gear has a structure in which a driven side and a fixed side of two internal gears are exchanged.
Or the electric flow regulating valve according to 9. 11. An annular concave portion provided on an inner peripheral portion of the pipe, an annular convex portion provided on an outer peripheral portion of the reduction gear casing, and slidably fitted in the concave portion. A solid lubricating film made of di-mobilized molybdenum, fluororesin, or the like provided on at least one of the outer peripheral surface and the inner peripheral surface of the concave portion; and a bias for urging the convex portion in the axial direction to press against the inner surface of the concave portion. The electric flow regulating valve according to any one of claims 7 to 10, further comprising means. 12. A first permanent magnet that is magnetized at least in a single pole in an axial direction between an output shaft of the reduction gear and the moving mechanism, and a magnetic material or the first permanent magnet and a different pole. The motor-operated flow control valve according to any one of claims 1 to 11, wherein the motor is connected by a magnetic coupling mechanism including a second permanent magnet that is magnetized to have at least a single pole in the axial direction such that: 13. A solid lubricating film made of mobilized molybdenum, fluororesin, or the like is provided on an abutting surface of the first permanent magnet and the magnetic body or the second permanent magnet. The electric flow regulating valve according to claim 12, wherein: 14. A third permanent magnet provided at a radially outer end of the convex portion of the moving element of the moving mechanism, and a position facing the third permanent magnet at an outer peripheral portion of the pipe. The motorized flow control valve according to any one of claims 1 to 13, further comprising: a magnetic detection element provided in (1). 15. A refrigeration cycle apparatus having a compressor, a condenser, an expander, and an evaporator in that order, and having a differential pressure regulating valve on an inlet side or an outlet side of the expander. Item 15. A refrigeration cycle apparatus using the electric flow control valve according to any one of Items 1 to 14.