JP2020173004A - Electric-operated valve and refrigeration cycle system - Google Patents

Abstract

To reduce slide resistance between a needle valve 4 and a main valve element 3 to reduce an operation load and perform proper flow control in an electric-operated valve which opens or closes a sub valve port 33a with the needle valve 4 and opens or closes a main valve port 13a with the main valve element 3 in which the needle valve 4 is installed.SOLUTION: An electric-operated valve includes: a main valve element 3 which opens or closes a main valve port 13a of a main valve chamber 1R; a needle valve 4 which changes an opening of a sub valve port 33a of the main valve element 3; and a driving part 5 which drives the needle valve 4 to move forward or rearward in an axis L direction through a screw feeding mechanism 5B by rotation of a magnet rotor 52. The needle valve 4 is inserted into a sub valve guide hole 32a of the main valve element 3, and a lubricative member 10 is provided between the sub valve guide hole 32a and the needle valve 4. The needle valve 4 and the main valve element 3 can slide relative to each other in the axis L direction through the lubricative member 10.SELECTED DRAWING: Figure 1

Description

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

Conventionally, as an electric valve provided in a refrigeration cycle of an air conditioner, there is an electric valve that opens and closes a sub-valve port with a sub-valve body and opens and closes a main valve port with a main valve body having the sub-valve body built therein. Such an electric valve is disclosed in, for example, Japanese Patent Application Laid-Open No. 6-24282 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2007-24186 (Patent Document 2).

Jikkenhei 6-24282 Japanese Unexamined Patent Publication No. 2007-24186

In an electric valve that opens and closes the sub-valve port with the sub-valve body and opens and closes the main valve port with the main valve body containing this sub-valve body, the sub-valve body is fixed or connected to the rotor shaft of the rotating rotor and driven. The rotation of the rotor of the part causes the auxiliary valve body to move forward and backward in the axial direction via the screw feed mechanism. For example, in Patent Document 2, the auxiliary valve port (small diameter valve port) is fully opened, and the auxiliary valve body (second valve body) lifts the main valve body (first valve body) via a slip washer. , The main valve port (large diameter valve port) begins to open. At this time, the slippery washer reduces the frictional force between the auxiliary valve body and the main valve body so that the rotation of the auxiliary valve body is not transmitted to the main valve body, thereby reducing the operating load. As described above, the main valve body needs to hold the sub valve body coaxially with the sub valve port of the main valve body. Therefore, a portion that slides or comes into contact between the outer peripheral portion of the sub-valve body and the peripheral portion inside the main valve body is generated, and a sliding resistance is generated between the sub-valve body and the main valve body. For example, the working load of sliding in the axial direction of the auxiliary valve body and sliding in the rotational direction around the axis increases. Further, there is a problem that the rotation of the sub-valve body is hindered by the inclination of the sub-valve body and the main valve body, and it becomes difficult to perform appropriate flow rate control.

The present invention is an electric valve that opens and closes a sub-valve port with a sub-valve body and opens and closes a main valve port with a main valve body containing the sub-valve body. The problem is to reduce the operating load and to control the flow rate appropriately.

The motorized valve of the present invention includes a main valve body that opens and closes the main valve port of the main valve chamber, a sub valve body that changes the opening degree of the sub valve port of the sub valve chamber provided in the main valve body, and a rotor. The sub-valve is provided with a drive unit that drives the sub-valve body to advance and retreat in the axial direction of the main valve port via a screw feed mechanism by rotation, and the sub-valve is in a state where the main valve body closes the main valve port. A small flow rate control range in which the body changes the opening degree of the auxiliary valve port, and a large flow rate control range in which the main valve body changes the opening degree of the main valve port and the main valve port is fully opened. An electric valve having a two-stage flow control range, wherein the sub-valve body is inserted into the main valve body, and a lubricating member is provided between the main valve body and the sub-valve body. The sub-valve body is slidably held inside the main valve body only by the lubricating member in the axial direction at least with respect to the main valve body, and the sub-valve body and the main valve body are formed by the lubricating member. It is characterized in that it is slidable with each other in the axial direction via the above.

According to the present invention as described above, the sub-valve body can freely slide in the axial direction in, for example, the sub-valve guide hole of the main valve body only through the lubricating member, and this sub-valve body is the main valve body. And its auxiliary valve port are coaxially guided on the axis. In addition, even if the sub-valve body rotates with the rotor, the lubricating member allows the sub-valve body to rotate freely inside the main valve body, so that sliding resistance can be reduced, the operating load is reduced, and appropriate flow rate control is performed. be able to.

Further, the lubricating member is interposed between the sub-valve body and the main valve body, and as a lubricious washer that transmits the advance / retreat drive of the sub-valve body in the axial direction to the main valve body. It is preferable that it is provided.

At this time, the auxiliary valve body has a guide boss portion formed integrally with the rotor shaft of the rotor, and the lubricating member is between the engaging portion on the main valve body side and the guide boss portion. It is preferable that the base portion provided as the washer is interposed in the base portion and the sleeve extends from the base portion to the outer periphery of the guide boss portion. As a result, the rotation around the axis between the guide boss portion of the auxiliary valve body and the engaging portion on the main valve body side becomes slidable.

Further, it is preferable that the sub-valve body rotates together with the rotor and the sub-valve body slides in the rotation direction in the main valve body via the lubricating member.

It is preferable that the lubricating member is made of a self-lubricating resin. The lubricating member is preferably a self-lubricating resin such as a fluororesin, PA (polyamide), PP (polypropylene), PPS (polyphenylene sulfide) or the like. As a specific example of the fluororesin, PTFE (polytetrafluoroethylene) or the like can be considered.

Further, it is preferable that the lubricating member is a member in which the surface of the base material is coated with a self-lubricating resin.

The refrigeration cycle system of the present invention includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and the indoor heat. A refrigeration cycle system including a dehumidifying valve provided in an exchanger, characterized in that any of the above electric valves is used as the dehumidifying valve.

Further, the refrigeration cycle system of the present invention includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger. It is a refrigeration cycle system, characterized in that any of the above electric valves is used as the electronic expansion valve.

According to such a refrigeration cycle system, similar to the effect of the above-mentioned motorized valve, the sliding resistance is reduced, the operating load is reduced, and appropriate flow rate control can be performed.

According to the motorized valve and the refrigeration cycle system of the present invention, in an electric valve having a two-stage flow rate control range, the operating load can be reduced and appropriate flow rate control can be performed.

It is a vertical cross-sectional view of the small flow rate control region state of the electric valve of 1st Embodiment of this invention. It is a vertical cross-sectional view of the main part in the fully opened state of the main valve body of the electric valve of 1st Embodiment. It is a side view and the plan view of the lubrication member in the motorized valve of 1st Embodiment. It is a vertical cross-sectional view of a main part in a state where the main valve body is started to be pulled up by the needle valve of the electric valve of the second embodiment of the present invention. It is a side view and the plan view of the lubrication member in the electric valve of 2nd Embodiment. It is a vertical cross-sectional view of a main part in a state where the main valve body is started to be pulled up by the needle valve of the motorized valve of the third embodiment of the present invention. It is a vertical cross-sectional view of a main part in a state where the main valve body is started to be pulled up by the needle valve of the motorized valve of the fourth embodiment of the present invention. It is a vertical cross-sectional view of a main part in a state where the main valve body is started to be pulled up by the needle valve of the electric valve of the fifth embodiment of the present invention. It is a vertical cross-sectional view of a main part in a state where the main valve body is started to be pulled up by the needle valve of the motorized valve of the sixth embodiment of the present invention. It is a figure which shows the refrigeration cycle system of embodiment of this invention.

Next, an embodiment of the motorized valve and the refrigeration cycle system of the present invention will be described with reference to the drawings. FIG. 1 is a vertical cross-sectional view of the motorized valve of the first embodiment in a small flow rate control range state, FIG. 2 is a vertical cross-sectional view of a main part of the motorized valve of the first embodiment in a fully open state, and FIG. 1 is a side view (FIG. 3 (A)) and a plan view (FIG. 3 (B)) of a lubricating member in the motorized valve of the first embodiment. The concept of "up and down" in the following description corresponds to the top and bottom in the drawings of FIGS. 1 and 2. The motorized valve 100 includes a valve housing 1, a guide member 2, a main valve body 3, a needle valve 4 as a "secondary valve body", and a drive unit 5.

The valve housing 1 is formed of, for example, brass, stainless steel, or the like in a substantially cylindrical shape, and has a main valve chamber 1R inside the valve housing 1. A first joint pipe 11 conducting to the main valve chamber 1R is connected to one side of the outer circumference of the valve housing 1, and a second joint pipe 12 is connected to a tubular portion extending downward from the lower end. Further, a cylindrical main valve seat 13 is formed on the main valve chamber 1R side of the second joint pipe 12 of the valve housing 1, and the inside of the main valve seat 13 is the main valve port 13a, and the second joint The pipe 12 is conducted to the main valve chamber 1R via the main valve port 13a. The main valve port 13a is a cylindrical through hole (through hole) centered on the axis L. The first joint pipe 11 and the second joint pipe 12 are fixed to the valve housing 1 by brazing or the like.

A guide member 2 is attached to the opening at the upper end of the valve housing 1. The guide member 2 includes a press-fitting portion 21 to be press-fitted into the inner peripheral surface of the valve housing 1, substantially cylindrical guide portions 22 and 23 having a diameter smaller than the press-fitting portion 21 and located above and below the press-fitting portion 21, and an upper guide. It has a holder portion 24 extending above the portion 22 and a ring-shaped flange portion 25 provided on the outer periphery of the press-fitting portion 21. The press-fitting portion 21, the guide portions 22, 23, and the holder portion 24 are configured as an integral product made of resin. Further, the flange portion 25 is, for example, a metal plate such as brass or stainless steel, and the flange portion 25 is integrally provided together with the resin press-fitting portion 21 by insert molding.

The guide member 2 is assembled to the valve housing 1 by the press-fitting portion 21, and is fixed to the upper end portion of the valve housing 1 via the flange portion 25 by welding. Further, in the guide member 2, a cylindrical main valve guide hole 2A coaxial with the axis L is formed inside the press-fitting portion 21 and the upper and lower guide portions 22 and 23, and a main valve guide hole 2A is formed in the center of the holder portion 24. A female screw portion 24a coaxial with the valve guide hole 2A and a screw hole thereof are formed. The main valve body 3 is arranged inside the main valve guide hole 2A inside the lower guide portion 23.

The main valve body 3 includes a main valve portion 31 that seats and departs from the main valve seat 13, a holding portion 32 having a columnar needle guide hole 32a, and a sub valve seat that constitutes the bottom of the needle guide hole 32a. It has 33 and a retainer 34 as an "engagement portion on the main valve body side" provided at the end portion of the holding portion 32 on the drive portion 5 side. A part of the lower side of the needle guide hole 32a is an auxiliary valve chamber 3R. In the needle guide hole 32a of the holding portion 32, the lubricating member 10 attached to the needle valve 4 described later and the guide boss portion 42 integrally formed with the rotor shaft 51 are inserted and ring-shaped. The retainer 34 is fixed to the upper end of the holding portion 32 by fitting or welding or welding.

Further, a main valve spring 3a is arranged between the retainer 34 and the upper end of the main valve guide hole 2A, and the main valve body 3 is directed toward the main valve seat 13 (closing direction) by the main valve spring 3a. ) Is being urged. A cylindrical sub-valve port 33a centered on the axis L is formed at the center of the sub-valve seat 33. Further, a conduction hole 32b for conducting the sub-valve chamber 3R and the main valve chamber 1R is formed at at least one position on the side surface of the holding portion 32, and the needle valve 4 as the sub-valve body serves the sub-valve port 33a. When opened, the main valve chamber 1R, the sub-valve chamber 3R, the sub-valve port 33a, and the main valve port 13a are electrically connected.

The needle valve 4 is formed integrally with the rotor shaft 51 and a truncated cone-shaped needle portion 41 formed integrally with the rotor shaft 51 at the lower end of the rotor shaft 51, which will be described later, and whose diameter gradually decreases toward the tip. A cylindrical guide boss portion 42 and the cylindrical guide boss portion 42 are integrally formed and provided. Further, a lubrication member 10 made of a self-lubricating resin (see Examples) is attached to the needle valve 4 so as to engage the rotor shaft 51 and the guide boss portion 42. Then, the lubricating member 10 and the guide boss portion 42 are inserted into the needle guide hole 32a, and the lubricating member 10 slides with respect to the inner peripheral surface of the needle guide hole 32a and the outer peripheral surface of the guide boss portion 42. It is possible. Since the outer diameter of the outer peripheral portion of the guide boss portion 42 is smaller than the inner diameter of the inner peripheral surface of the needle guide hole 32a, the guide is larger than the frictional force between the main valve body 3 and the lubricating member 10. Since the frictional force between the boss portion 42 and the lubricating member 10 is smaller, the guide boss portion 42 tends to rotate with respect to the lubricating member 10.

As shown in FIG. 3, the lubricating member 10 is provided on the outer periphery of the base portion 10a that engages with the rotor shaft 51 via the U-shaped notch 10a1 and the guide boss portion 42 in the axis L direction from the base portion 10a. It is composed of an extending sleeve 10b.

A case 14 is airtightly fixed to the upper end of the valve housing 1 by welding or the like, and a drive unit 5 is formed inside and outside the case 14. The drive unit 5 includes a stepping motor 5A, a screw feed mechanism 5B that advances and retreats the needle valve 4 by the rotation of the stepping motor 5A, and a stopper mechanism 5C that regulates the rotation of the stepping motor 5A.

The stepping motor 5A includes a rotor shaft 51, a magnet rotor 52 rotatably arranged inside the case 14, a stator coil 53 arranged to face the magnet rotor 52 on the outer circumference of the case 14, and others shown in the figure. It is composed of a yoke, exterior members, etc. The rotor shaft 51 is attached to the center of the magnet rotor 52 via a bush, and a male screw portion 51a is formed on the outer periphery of the rotor shaft 51 on the guide member 2 side. The male threaded portion 51a is screwed into the female threaded portion 24a of the guide member 2, whereby the guide member 2 supports the rotor shaft 51 on the axis L. The female screw portion 24a of the guide member 2 and the male screw portion 51a of the rotor shaft 51 form the screw feed mechanism 5B.

With the above configuration, when the stepping motor 5A is driven, the magnet rotor 52 and the rotor shaft 51 rotate, and the magnet rotor 52 is provided by the screw feed mechanism 5B between the male screw portion 51a of the rotor shaft 51 and the female screw portion 24a of the guide member 2. At the same time, the rotor shaft 51 moves in the L direction of the axis. Then, the needle valve 4 moves back and forth in the axis L direction, and the needle valve 4 approaches or separates from the auxiliary valve port 33a. Further, when the needle valve 4 rises, the lubricating member 10 engages with the retainer 34 of the main valve body 3, and the main valve body 3 moves together with the needle valve 4 and separates from the main valve seat 13. A protrusion 52a is formed on the magnet rotor 52, and the protrusion 52a operates the rotation stopper mechanism 5C as the magnet rotor 52 rotates, and the lowermost position of the rotor shaft 51 (and the magnet rotor 52) and the lowermost position and the magnet rotor 52. The topmost position is regulated. Further, when the needle valve 4 rises and the lubricating member 10 engages with the retainer 34 and the main valve body 3 rises, the lubricating member 10 acts as a lubricious washer, so that the needle valve 4 rotates. Is not transmitted to the main valve body 3, so that the operating load is reduced.

In the small flow rate control range state of FIG. 1, the main valve body 3 is seated on the main valve seat 13, the main valve port 13a is closed, and the needle valve 4 controls the opening degree of the sub valve port 33a, resulting in a small flow rate. Is controlled. Further, for example, when the needle valve 4 and the main valve body 3 are raised while the compressor of the refrigeration cycle system is stopped and the fluid (refrigerant) is stopped, the main valve port 13a is fully opened. As a result, a large flow rate of fluid (refrigerant) is flowed from the second joint pipe 12 to the first joint pipe 11 during the heating operation.

As described above, the needle valve 4 (sub-valve body) is inserted into the sub-valve guide hole 32a of the main valve body 3, and the lubricating member 10 is provided between the sub-valve guide hole 32a and the needle valve 4. Has been done. Then, the needle valve 4 and the main valve body 3 are slidable with each other in the axis L direction via the lubricating member 10. That is, the needle valve 4 can freely slide in the auxiliary valve guide hole 32a of the main valve body 3 in the axis L direction via the lubricating member 10, and the needle valve 4 has the main valve body 3 and the auxiliary valve port. It is guided coaxially on the axis L with respect to 33a. Further, even if the needle valve 4 rotates together with the magnet rotor 52 and the rotor shaft 51, the needle valve 4 can freely rotate in the sub-valve guide hole 32a of the main valve body 3 by the lubricating member 10. Therefore, the sliding resistance with the main valve body 3 can be reduced, and the operating load is reduced. In addition, the posture of the main valve body 3 can be stabilized and appropriate flow rate control can be performed.

4 and 6 to 9 are vertical cross-sectional views of main parts of the motorized valves of the second to sixth embodiments. The difference between the second to sixth embodiments and the first embodiment is the lubrication member and its mounting structure, and the same elements as those in the first embodiment are designated by the same reference numerals as those in FIGS. 1 to 3 and overlapped. The description will be omitted as appropriate. Note that FIGS. 4, 6, 7, 8 and 9 show a state in which the needle valve 4 starts pulling up the main valve body 3.

In the second embodiment of FIG. 4, a lubrication member 20 made of a self-lubricating resin (see Examples) is attached to the needle valve 4 so as to engage the rotor shaft 51 and the guide boss portion 42. There is. Then, the lubricating member 20 and the guide boss portion 42 are inserted into the needle guide hole 32a, and the lubricating member 20 slides with respect to the inner peripheral surface of the needle guide hole 32a and the outer peripheral surface of the guide boss portion 42. It is possible.

As shown in FIG. 5, the lubricating member 20 includes a base portion 20a having an insertion hole 20a1 fitted to the rotor shaft 51, and a sleeve 20b extending from the base portion 20a to the outer periphery of the guide boss portion 42 in the axis L direction. It is composed of and. The insertion hole 20a1 of the base portion 20a has a diameter slightly larger than the outer diameter of the male screw portion 51a of the rotor shaft 51. As a result, the lubricating member 20 is fitted from the upper end side of the rotor shaft 51, and the sleeve 20b is engaged with the outer circumference of the guide boss portion 42.

In this second embodiment as well, as in the first embodiment, the needle valve 4 can freely slide in the auxiliary valve guide hole 32a of the main valve body 3 in the axis L direction via the lubricating member 20. The needle valve 4 is coaxially guided on the axis L with respect to the main valve body 3 and the sub valve port 33a. Further, even if the needle valve 4 rotates, the lubrication member 20 allows the needle valve 4 to freely rotate in the sub-valve guide hole 32a of the main valve body 3. Further, as in the first embodiment, the lubricating member 20 acts as a lubricating washer when engaged with the retainer 34, so that the rotation of the needle valve 4 is not transmitted to the main valve body 3 and is operated. The load is reduced. Therefore, the sliding resistance with the main valve body 3 can be reduced, and the operating load is reduced. In addition, the posture of the main valve body 3 can be stabilized and appropriate flow rate control can be performed.

In the third embodiment of FIG. 6, the diameter of the guide boss portion 42'of the needle valve 4 is smaller than that of the first embodiment, and the outer circumference thereof is made of a cylindrical self-lubricating resin (see Examples) for lubricity. The member 30 is fitted and attached. Further, a washer 301 is arranged between the guide boss portion 42'and the retainer 34. Then, the lubricating member 30 and the guide boss portion 42'are inserted into the needle guide hole 32a, and the lubricating member 30 is inserted into the inner peripheral surface of the needle guide hole 32a and the outer peripheral surface of the guide boss portion 42'. It is slidable.

Also in this third embodiment, as in the first embodiment, the needle valve 4 can freely slide in the auxiliary valve guide hole 32a of the main valve body 3 in the axis L direction via the lubricating member 30. The needle valve 4 is coaxially guided on the axis L with respect to the main valve body 3 and the sub valve port 33a. Further, even if the needle valve 4 and the lubricating member 30 rotate, the needle valve 4 and the lubricating member 30 can freely rotate in the sub-valve guide hole 32a of the main valve body 3. Therefore, the sliding resistance with the main valve body 3 can be reduced, and the operating load is reduced. In addition, the posture of the main valve body 3 can be stabilized and appropriate flow rate control can be performed.

In the fourth embodiment of FIG. 7, the needle valve 4 does not have a guide boss portion, and a lubricating member 40 made of a cylindrical self-lubricating resin (see Examples) is fitted on the outer periphery of the rotor shaft 51. It is installed together. Further, a C-ring 401 for preventing the slip-out is fixed to the rotor shaft 51 at the lower part of the lubricating member 40. The C ring 401 may be integrated with the rotor shaft 51. The lubricating member 40 is inserted into the needle guide hole 32a, and the lubricating member 40 is slidable with respect to the inner peripheral surface of the needle guide hole 32a and the outer peripheral surface of the rotor shaft 51.

In this fourth embodiment as well, as in the first embodiment, the needle valve 4 can freely slide in the auxiliary valve guide hole 32a of the main valve body 3 in the axis L direction via the lubricating member 40. The needle valve 4 is coaxially guided on the axis L with respect to the main valve body 3 and the sub valve port 33a. Further, even if the needle valve 4 rotates, the lubrication member 40 allows the needle valve 4 to freely rotate in the sub-valve guide hole 32a of the main valve body 3. Further, as in the first embodiment, the lubricating member 40 acts as a lubricating washer when engaged with the retainer 34, so that the rotation of the needle valve 4 is not transmitted to the main valve body 3 and is operated. The load is reduced. Therefore, the sliding resistance with the main valve body 3 can be reduced, and the operating load is reduced. In addition, the posture of the main valve body 3 can be stabilized and appropriate flow rate control can be performed.

In the fifth embodiment of FIG. 8, the needle valve 4 does not have a guide boss portion, and a lubricating member 50 made of a cylindrical self-lubricating resin (see Examples) is fitted on the outer periphery of the rotor shaft 51. It is installed together. Further, in the rotor shaft 51, a step portion 511 is formed at the upper end portion of the lubrication member 50, and a C ring 501 for preventing the lubrication member 50 is fixed to the rotor shaft 51 at the lower portion of the lubrication member 50. As a result, the lubricating member 50 is fixed to the rotor shaft 51 (and the needle valve 4). The lubricating member 50 is inserted into the needle guide hole 32a, and the lubricating member 50 is slidable with respect to the inner peripheral surface of the needle guide hole 32a and the outer peripheral surface of the rotor shaft 51. The lubricating member 50 may be fixed so as to be rotatable with respect to the rotor shaft 51.

In the fifth embodiment as well, as in the first embodiment, the needle valve 4 can freely slide in the auxiliary valve guide hole 32a of the main valve body 3 in the axis L direction via the lubricating member 50. The needle valve 4 is coaxially guided on the axis L with respect to the main valve body 3 and the sub valve port 33a. Further, even if the needle valve 4 and the lubricating member 50 rotate, the needle valve 4 and the lubricating member 50 can freely rotate in the sub-valve guide hole 32a of the main valve body 3. Further, as in the first embodiment, the lubricating member 50 acts as a lubricating washer when engaged with the retainer 34, so that the rotation of the needle valve 4 is not transmitted to the main valve body 3 and is operated. The load is reduced. Therefore, the sliding resistance with the main valve body 3 can be reduced, and the operating load is reduced. In addition, the posture of the main valve body 3 can be stabilized and appropriate flow rate control can be performed.

In the sixth embodiment of FIG. 9, a lubrication member 60 made of a self-lubricating resin (see Examples) is attached to the needle valve 4 so as to engage the rotor shaft 51 and the guide boss portion 42. There is. The lubricity member 60 is composed of a base portion 60a having an insertion hole 60a1 that fits into the rotor shaft 51, and a sleeve 60b extending from the base portion 60a to the outer periphery of the guide boss portion 42 in the axis L direction. The insertion hole 60a1 of the base portion 60a has a diameter slightly larger than the outer diameter of the male screw portion 51a of the rotor shaft 51. As a result, the lubricating member 60 is fitted from the upper end side of the rotor shaft 51, and the sleeve 60b is engaged with the outer circumference of the guide boss portion 42. Further, the main valve body 3 is formed with a fitting hole 32a'similar to the needle guide hole 32a of the above embodiment, and a step portion 32a1'is formed in the fitting hole 32a'. As a result, the lubricating member 60 is fixed inside the main valve body 3. The lubricating member 60 may be fixed to the main valve body 3 so as to be rotatable.

Also in the sixth embodiment, as in the first embodiment, the needle valve 4 (the boss portion 42 for guiding the needle valve 4) can freely slide in the axis L direction inside the sleeve 60b of the lubricating member 60. The needle valve 4 is coaxially guided on the axis L with respect to the main valve body 3 and the sub valve port 33a. Further, even if the needle valve 4 rotates due to the lubricating member 60, it can freely rotate inside the main valve body 3. Further, as in the first embodiment, the lubricating member 60 acts as a lubricating washer when engaged with the retainer 34, so that the rotation of the needle valve 4 is not transmitted to the main valve body 3 and is operated. The load is reduced. Therefore, the sliding resistance with the main valve body 3 can be reduced, and the operating load is reduced. In addition, the posture of the main valve body 3 can be stabilized and appropriate flow rate control can be performed.

Next, the refrigeration cycle system of the present invention will be described with reference to FIG. Refrigeration cycle systems are used, for example, in air conditioners such as home air conditioners. The electric valve 100 of each of the above embodiments is between the first indoor side heat exchanger 91 (operating as a dehumidifying cooler) and the second indoor side heat exchanger 92 (operating as a dehumidifying heater) of the air conditioner. A heat pump type refrigeration cycle is formed together with a compressor 95, a four-way valve 96, an outdoor heat exchanger 94 and an electronic expansion valve 93. The first indoor side heat exchanger 91, the second indoor side heat exchanger 92, and the electric valve 100 are installed indoors, and the compressor 95, the four-way valve 96, the outdoor heat exchanger 94, and the electronic expansion valve 93 are installed outdoors. It constitutes a heating and cooling system.

In the electric valve 100 of the embodiment as a dehumidifying valve, the main valve body is fully opened during cooling or heating other than during dehumidification, and the first chamber heat exchanger 91 and the second chamber heat exchanger 92 are in one chamber. It is said to be a heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 alternately function as an "evaporator" and a "condenser". That is, the electric valve 93 as the electronic expansion valve is provided between the evaporator and the condenser.

The above refrigeration cycle system is an example in which the electric valve of the present invention is used as a dehumidifying valve, but the electric valve of the present invention can also be applied to the electric valve 93 as the above-mentioned electronic expansion valve. In this case, the dehumidifying valve may or may not be provided.

The materials of the lubricating members 10 to 60 of each embodiment are preferably as follows. For example, a self-lubricating resin such as a fluororesin, PA (polyamide), PP (polypropylene), PPS (polyphenylene sulfide) is preferable. As a specific example of the fluororesin, PTFE (polytetrafluoroethylene) or the like can be considered. Further, the lubricating members 10 to 60 may be a base material such as metal or resin coated with the above-mentioned self-lubricating resin.

The present invention is not limited to the above-described embodiment, but includes other configurations and the like that can achieve the object of the present invention, and the following modifications and the like are also included in the present invention. For example, in the above embodiment, the electric valve 100 used in an air conditioner such as a home air conditioner has been illustrated, but the electric valve of the present invention is not limited to a home air conditioner and may be a commercial air conditioner. It can be applied not only to air conditioners but also to various refrigerators.

The embodiments of the present invention have been described in detail with reference to the drawings, and other embodiments have also been described in detail. However, the specific configuration is not limited to these embodiments, and the present invention is not limited to these embodiments. It is included in the present invention even if there is a design change or the like within a range that does not deviate from the gist.

1 Valve housing 1R Main valve chamber 11 1st joint pipe 12 2nd joint pipe 13 Main valve seat 13a Main valve port 14 Case L Axis 2 Guide member 2A Main valve guide hole 21 Press-fitting part 22 Upper guide part 23 Lower guide Part 231 Contact part 24 Holder part 24a Female thread part 25 Flange part 3 Main valve body 3a Main valve spring 3R Sub valve chamber 31 Main valve part 311 Contact part 32 Holding part 32a Needle guide hole 32b Conduction hole 33 Sub valve seat 33a Sub Valve port 34 retainer (engagement on the main valve body side)
4 Needle valve (secondary valve body)
41 Needle part 42 Guide boss part 5 Drive part 5A Stepping motor 5B Screw feed mechanism 5C Stopper mechanism 51 Rotor shaft 51a Male thread part 52 Magnet rotor 52a Protrusion part 53 Stator coil 10 Lubrication member 20 Lubrication member 30 Lubrication member 40 Lubrication Sex member 50 Lubricating member 60 Lubricating member 91 1st indoor side heat exchanger 92 2nd indoor side heat exchanger 93 Electronic expansion valve 94 Outdoor heat exchanger 95 Compressor 96 Four-way valve 100 Electric valve

Claims (8)

A main valve body that opens and closes the main valve port of the main valve chamber, a sub valve body that changes the opening degree of the sub valve port of the sub valve chamber provided in the main valve body, and a screw feed mechanism by rotating the rotor. The sub-valve body is provided with a drive unit that drives the sub-valve body to move forward and backward in the axial direction of the main valve port, and the sub-valve body is a sub-valve port with the main valve body closed. A two-stage flow rate control area consisting of a small flow rate control area for changing the opening degree and a large flow rate control area where the main valve body changes the opening degree of the main valve port and the main valve port is fully opened. It is an electric valve that has
The sub-valve body is inserted into the main valve body, and a lubricating member is provided between the main valve body and the sub-valve body, and the sub-valve body has the lubricity inside the main valve body. The member alone slides and holds the main valve body at least in the axial direction, and the sub-valve body and the main valve body become slidable with each other in the axial direction via the lubricating member. An electric valve characterized by being lubricated. The lubricating member is interposed between the sub-valve body and the main valve body, and is provided as a lubricious washer that transmits the advance / retreat drive of the sub-valve body in the axial direction to the main valve body. The electric valve according to claim 1, wherein the valve is characterized by the above. The sub-valve body has a guide boss portion formed integrally with the rotor shaft of the rotor, and the lubricating member is interposed between the engagement portion on the main valve body side and the guide boss portion. The electric valve according to claim 2, wherein the electric valve is composed of a base portion provided as a washer and a sleeve extending from the base portion to the outer periphery of the guide boss portion. Claims 1 to 3 are characterized in that the sub-valve body rotates together with the rotor and the sub-valve body slides in the rotation direction in the main valve body via the lubricating member. The electric valve according to any one of the above. The motorized valve according to any one of claims 1 to 4, wherein the lubricating member is made of a self-lubricating resin. The motorized valve according to any one of claims 1 to 4, wherein the lubricating member is a member in which the surface of a base material is coated with a self-lubricating resin. A compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and a dehumidifying valve provided in the indoor heat exchanger. A refrigeration cycle system comprising the above, wherein the electric valve according to any one of claims 1 to 6 is used as the dehumidifying valve. A refrigeration cycle system including a compressor, an indoor heat exchanger, an outdoor heat exchanger, and an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger. A refrigeration cycle system according to any one of 6 to 6, wherein the electric valve is used as the electronic expansion valve.

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