JP2021080982A - Motor valve and refrigeration cycle system - Google Patents

Abstract

To provide a motor valve having a two-stage flow rate control region in which a main valve body is in a seated state on a main valve seat, and a flow rate control is performed in a small flow rate control region for a coolant by an orifice between an auxiliary valve port and a needle valve formed on the main valve body, in which a controllability in the small flow rate region is improved even when the main valve body vibrates in the small flow rate control region.SOLUTION: A columnar straight part 3S parallel with an axial line L is formed at an end part of a main valve part 31 of a main valve body 3. In a state where a main valve port 13a is fully closed in the main valve body 3, fluid is caused to flow through an orifice (gap) between a needle part 42 of a needle valve 4 and an auxiliary valve port 33a to form a small flow rate control region. In the small flow rate control region. a cross section of a gap between the straight part 3S of the main valve body 3 and the main valve port 13a is made constant.SELECTED DRAWING: Figure 4

Description

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

Conventionally, as an electric valve provided in a refrigeration cycle of an air conditioner, there is an electric valve that controls the flow rate in a small flow rate control range and a large flow rate range. Such an electric valve has an application to be mounted on an indoor unit (for example, a dehumidifying valve), and is disclosed in, for example, Japanese Patent Application Laid-Open No. 2019-132347 (Patent Document 1).

Japanese Unexamined Patent Publication No. 2019-132347

In this type of electric valve, for example, a dehumidifying operation is performed in the small flow rate control range. In this small flow rate control range, the main valve port of the main valve seat is fully closed by the main valve body, and the main valve body is set to this main valve body. The refrigerant is configured to pass through the throttle portion between the formed auxiliary valve port and the needle valve (secondary valve body). However, there is a problem that the main valve body vibrates due to pressure change and pipe vibration caused by the pulsation of the refrigerant flow on the primary side or the secondary side. Normally, in this small flow rate control range, the main valve body has the main valve port fully closed, but the main valve body may be lifted from the main valve port (main valve seat) due to the above vibration. Therefore, there is a problem that the flow rate of the fluid increases / decreases (varies) according to the amount of increase of the main valve body.

In the present invention, the main valve body is seated on the main valve seat, and the flow rate is controlled in the small flow rate control range of the refrigerant by the throttle portion between the auxiliary valve port and the needle valve formed in the main valve body. In an electric valve having a step flow rate control range, it is an object to improve the controllability of the small flow rate range even if there is vibration of the main valve body in the small flow rate control range.

The electric valve of the present invention includes a main valve body that is close to or separated from the main valve seat formed on the periphery of the main valve port provided in the main valve chamber of the valve body in the axial direction of the main valve port. At the same time, a sub-valve seat formed on the periphery of a sub-valve port provided in the sub-valve chamber inside the main valve body is provided with a sub-valve seat that is close to or separated from the sub-valve seat, and the sub-valve body holds the main valve body. It is a two-stage electric valve configured to be pressed against the main valve seat, and is between the main valve body and the main valve seat within an allowable range of slight fluctuation in the axial direction of the main valve body. A straight portion parallel to the axis is provided on at least one of the main valve body and the main valve seat so as to keep the opening area of the main valve body constant.

At this time, the main valve body is provided with the columnar straight portion inserted into the main valve port, and the straight portion is a portion having the minimum diameter of the main valve port within the allowable range in the axial direction. An electric valve characterized by facing the above is preferable.

Further, the main valve port of the main valve seat constitutes the cylindrical straight portion through which a part of the main valve body is inserted, and the straight portion constitutes the main valve body within the allowable range in the axial direction. An electric valve characterized by facing the ridge in the main valve port is preferable.

Further, an electric valve characterized in that the sub-valve body is configured to press the main valve body against the main valve seat without contacting the sub-valve seat is preferable.

Further, the sub-valve body and the main valve body are provided with a contact portion, and one of the contact portions is a tapered portion whose central axis is the axis of the sub-valve port, and the other is a tapered portion whose central axis is the axis of the sub-valve port. An electric valve characterized by having a stepped portion is preferable.

Further, the contact portion between the sub-valve body and the main valve body is via a spring installed between a flange portion provided on the sub-valve body and a step portion provided on the main valve body. An electric valve characterized by being brought into contact with each other is preferable.

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 the electric valve is used as the dehumidifying valve.

According to the electric valve and the refrigeration cycle system of the present invention, in the state of small flow rate control by the throttle portion (gap) between the sub-valve body and the sub-valve port, the pressure change of the fluid and the vibration of the pipe at the main valve port occur. Even if the main valve body rises, the flow rate becomes constant within the permissible range of the straight portion, and the controllability in the small flow rate range is improved.

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 at the time of the operation stop or the cooling operation in the fully open state of the main valve body of the electric valve of 1st Embodiment. It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of 1st Embodiment. FIG. 5 is an enlarged vertical cross-sectional view of a main part in which the auxiliary valve body is slightly raised from the small flow rate control range state of FIG. 3 of the electric valve of the first embodiment. It is an enlarged view which shows the straight part and the seating part of the main valve body in the electric valve of 1st Embodiment. It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of the 2nd Embodiment. It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of the 3rd embodiment. It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of 4th Embodiment. It is an enlarged view which shows the straight part of the main valve seat in the electric valve of 4th Embodiment. It is a figure explaining the permissible range of the minute vibration of the electric valve of 5th Embodiment. It is an enlarged view which shows the straight part of the main valve seat in the electric valve of 5th Embodiment. It is a figure which shows the refrigeration cycle system of embodiment of this invention.

Next, an embodiment of the electric 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 electric valve of the first embodiment in a small flow rate control range state, and FIG. 2 is a vertical cross-sectional view of the electric valve of the first embodiment when the main valve body is fully open and the operation is stopped or during cooling operation. FIG. 3 is an enlarged vertical cross-sectional view of a main part of the small flow rate control range state of the electric valve of the first embodiment. ”FIG. 4 shows a state in which the auxiliary valve body is slightly raised from the small flow rate control range state of FIG. It is an enlarged vertical sectional view of the main part of. FIG. 5 (A) shows a state in which the main valve body floats from the main valve seat in the state of FIG. 4, and FIG. 5 (B) shows a stepped portion in the main valve body and a sub valve body in the state of FIG. It is a vertical cross-sectional view of a taper part (contact part). The concept of "upper and lower" in the following description corresponds to the upper and lower parts in the drawings of FIGS. 1 and 2. The electric 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 that is press-fitted into the inner peripheral surface of the valve housing 1, substantially cylindrical guide portions 22 and 23 that are smaller in diameter than the press-fitting portion 21 and are 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 flange portion 25 is provided with a hole (not shown) for communicating the main valve chamber 1R and the inside of the case 14, which will be described later, in the axis L direction of the valve shaft.

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 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 the guide hole 2A is formed in the center of the holder portion 24. A female screw portion 24a coaxial with the screw portion 24a and a screw hole thereof are formed. The main valve body 3 is arranged inside the 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 provided at the end of the holding portion 32. Further, below the needle guide hole 32a, there is an auxiliary valve chamber 3R connected to the needle guide hole 32a, and a step portion as an "contact portion" is formed at the boundary between the auxiliary valve chamber 3R and the needle guide hole 32a. 3a is formed. A washer 43 attached to the rotor shaft 51, which will be described later, and a guide boss portion 41 of the needle valve 4 integrally formed with the rotor shaft 51 are inserted into the needle guide hole 32a of the holding portion 32. The ring-shaped retainer 34 is fixed to the upper end of the holding portion 32 by fitting or welding.

Further, a main valve spring 35 is disposed between the retainer 34 and the upper end portion of the guide hole 2A, and the main valve body 3 is moved in the direction (closed direction) of the main valve seat 13 by the main valve spring 35. 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 auxiliary valve chamber 3R and the main valve chamber 1R is formed at one position on the side surface of the holding portion 32 below the step portion 3a, and the needle valve 4 as the auxiliary valve body 4 When the sub-valve port 33a is opened, the main valve chamber 1R, the sub-valve chamber 3R, the sub-valve port 33a, and the main valve port 13a become conductive. Further, the main valve chamber 1R and the inside of the case 14 are communicated with each other by a hole (not shown) communicating with the valve shaft in the axis L direction provided in the flange portion 25, and the inside of the case 14 and the inside of the guide member 2 are communicated with each other. It is communicated by a communication hole provided in the upper part of the guide member 2, and the space above the main valve body 3 and the step portion 3a of the main valve body 3 is the outer circumference of the washer 43 and the guide boss portion 41 of the needle valve 4. The main valve chamber 1R and the sub-valve chamber 3R communicate with each other by communicating with each other through a gap between the outer circumference and the inner circumference of the needle guide hole 32a of the main valve body 3.

The needle valve 4 as the "secondary valve body" is integrally formed with the rotor shaft 51 at the lower end of the rotor shaft 51, and the needle valve 4 is composed of a guide boss portion 41 and a needle portion 42. There is. The guide boss portion 41 has a tapered portion 41a as a truncated cone-shaped "contact portion" whose diameter gradually decreases toward the needle portion 42 side, and this taber portion 41a is a step portion 3a of the main valve body 3. It is possible to contact the (contact part). Further, the needle portion 42 is connected to the end portion of the tapered portion 41a. An annular washer 43 made of a lubricating resin is disposed at the upper end of the guide boss portion 41. The washer 43 and the guide boss portion 41 are slidably inserted into the needle guide hole 32a.

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 circumference 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. Further, a coil spring 55 is arranged in a cylindrical portion 14a that holds the rotation stopper mechanism 5C on the inner ceiling portion of the case 14 via a spring receiver 54 that abuts on the upper end of the rotor shaft 51. By urging the rotor shaft 51 downward, backlash in the screw feed mechanism 5B is prevented.

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 washer 43 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.

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 shown in FIG. Become. As a result, a large flow rate of fluid (refrigerant) flows from the first joint pipe 11 to the second joint pipe 12 during the cooling operation, and a large flow rate flows from the second joint pipe 12 to the first joint pipe 11 during the heating operation. A fluid (refrigerant) is flowed.

As shown in FIGS. 3 and 4, the needle portion 42 is composed of a straight portion 42a formed of a cylinder whose center line is the axis L, and a needle 42b whose diameter is reduced toward the tip end side. Further, the outer diameter of the straight portion 42a is smaller than the inner diameter of the sub-valve port 33a, and a throttle portion (gap) is formed between the straight portion 42a and the sub-valve port 33a. Then, a small flow rate control is performed by flowing a constant flow rate of the refrigerant through the throttle portion. Further, in this small flow rate control state, the tapered portion 41a of the guide boss portion 41 of the needle valve 4 comes into contact with the stepped portion 3a of the main valve body 3. At this time, the needle valve 4 presses the main valve body 3 toward the main valve seat 13 by the urging force of the coil spring 55 for preventing backlash. Therefore, even if a slight pressure change of the fluid occurs between the main valve chamber 1R and the main valve port 13a, the main valve body 3 does not vibrate and the controllability in the small flow rate region is improved.

Here, as shown in FIG. 4, the needle 4 slightly rises from the stepped portion 3a of the main valve body 3 (L1 shown in FIG. 5B), and the tapered portion 41a of the needle valve 4 rises slightly from the stepped portion 3a of the main valve body 3. When the main valve body 3 is separated from the portion 3a, the main valve body 3 is urged in the direction (closing direction) of the main valve seat 13 by the main valve spring 35, so that the tapered portion 41a of the needle valve 4 is the main valve. Normally, the main valve body 3 maintains a seated state with respect to the main valve seat 13 even if it is not in contact with the stepped portion 3a of the body 3, but it is large due to pressure fluctuations of the first joint pipe 11 and the second joint pipe 12. When a pressure difference occurs, the main valve body 3 may rise a distance of L1 from the main valve seat 13. On the other hand, in the first embodiment, as shown in FIGS. 4 and 5A, a cylindrical straight portion 3S centered on the axis L is provided at the tip end portion of the main valve portion 31 of the main valve body 3. It is formed. The outer diameter of the straight portion 3S is slightly smaller than the inner diameter of the columnar main valve port 13a, and the straight portion 3S is inserted into the main valve port 13a. Here, L1 is the size of the backlash of the female threaded portion 24a and the male threaded portion 51a.

As a result, as shown in FIG. 5A, the gap between the outer circumference of the straight portion 3S and the main valve port 13a becomes a constant width within a certain allowable range L2 in the axis L direction. Here, the flow path area due to the gap between the outer circumference of the straight portion 3S and the main valve port 13a is the tapered portion 41a of the needle valve 4 when the needle valve 4 is levitated by the distance L1 shown in FIG. 5 (B). Is set smaller than the flow path area due to the stepped portion 3a of the main valve body 3. Further, when the main valve body 3 is seated on the main valve seat 13, the allowable range L2 is preferably the distance L1 between the tapered portion 41a and the stepped portion 3a shown in FIG. 5 (B).
L1 × 2>L2> L1
It is set to be. That is, the constant allowable range L2 in the axis L direction is set to be larger than the backlash of the female threaded portion 24a and the male threaded portion 51a and smaller than twice the backlash.

In this way, within the permissible range L2 of the slight fluctuation in the axis L direction of the main valve body 3, the opening area between the main valve body 3 and the main valve seat 13 is parallel to the axis L so as to be constant. A columnar straight portion 3S is provided on the main valve body 3, and the straight portion 3S is inserted into the main valve port 13a. Further, the straight portion 3S faces the portion having the minimum diameter of the main valve port 13a within the allowable range L2 in the axis L direction. As a result, even if the main valve body 3 floats with respect to the main valve seat 13 in the axis L direction, if the floating amount is within the allowable range L2, the gap between the straight portion 3S and the main valve seat 13 is provided. The opening area is constant. Therefore, even when the main valve body 3 vibrates, the flow rate of the fluid flowing from the first joint pipe 11 to the second joint pipe 12 can be kept constant, and the controllability in the small flow rate region is improved.

FIG. 6 is an enlarged vertical cross-sectional view of a main part of the electric valve of the second embodiment in the small flow rate control range state, and in each of the following embodiments, the overall configuration of the electric valve other than the characteristic portion of each embodiment is shown in FIG. It is the same as FIG. The needle valve 4'in the second embodiment includes a thin guide boss portion 41' (flange portion) integrally formed with the rotor shaft 51 and a needle as a "secondary valve body" similar to the first embodiment. It is composed of a portion 42 and a long truncated cone-shaped connecting rod 43', and the needle portion 42 is connected to an end portion of the connecting rod 43'. Further, a coil spring 7 is disposed between the guide boss portion 41'and the step portion 3a of the main valve body 3 via an annular spring receiver 7a made of a lubricating resin. The lower end of the coil spring 7 constitutes an "contact portion" that abuts on the step portion 3a.

With the above configuration, as in the first embodiment, small flow rate control is performed by flowing a constant flow rate of refrigerant through the throttle portion between the straight portion 42a of the needle portion 42 and the auxiliary valve port 33a, and this small flow rate is performed. In the controlled state, the needle valve 4'presses the main valve body 3 toward the main valve seat 13 by the urging force of the coil spring 7. Therefore, even if the pressure of the fluid changes between the main valve chamber 1R and the main valve port 13a, the main valve body 3 does not vibrate and the controllability in the small flow rate region is improved. That is, even if the main valve body 3 vibrates within the permissible range L2 when a large pressure difference occurs due to the pressure fluctuation, the controllability in the small flow rate region is improved as in the first embodiment. ..

FIG. 7 is an enlarged vertical cross-sectional view of a main part of the electric valve of the third embodiment in the small flow rate control range state. This third embodiment eliminates the configuration of pressing the main valve body 3 toward the main valve seat 13 like the tapered portion 41a and the stepped portion 3a of the first embodiment and the coil spring 7 of the second embodiment. is there. The needle valve 4 "in the third embodiment is formed at the lower end of the rotor shaft 51 with a columnar guide boss 41" integrally formed with the rotor shaft 51 and at the lower end of the guide boss 41 ". The needle valve 4 ″ is integrally formed with the needle portion 42 ″ as the “sub-valve body”, and the needle valve 4 ″ is provided with the washer 43 as in the above embodiment, and the washer 43 and the guide are provided. The boss portion 41 ″ is slidably inserted into the needle guide hole 32a.

Also in this third embodiment, as in the above embodiment, the small flow rate control is performed by flowing a constant flow rate of the refrigerant through the throttle portion between the straight portion 42a of the needle portion 42 and the auxiliary valve port 33a. The configuration of the main valve body 3 and the main valve seat 13 in the third embodiment is the same as that in the first embodiment, and the opening due to the gap between the straight portion 3S of the main valve body 3 and the main valve seat 13 is provided. The area becomes constant. That is, even if the main valve body 3 vibrates when a large pressure difference is generated due to the pressure fluctuation, the controllability in the small flow rate region is improved as in the first embodiment.

FIG. 8 is an enlarged vertical cross-sectional view of a main part of the electric valve of the fourth embodiment in the small flow rate control range state. In the fourth embodiment, the upper portion of the main valve port 13a of the main valve seat 13 is a straight portion 13S, and an annular protrusion centered on the axis L is formed on the outer periphery of the tip portion of the main valve portion 31 of the main valve body 3. It forms 31a. The outer diameter of the ridge 31a is slightly smaller than the inner diameter of the cylindrical straight portion 13S (main valve port 13a), and the ridge 31a is inserted into the straight portion 13S.

As a result, as shown in FIG. 9, the gap between the outer circumference of the ridge 31a and the straight portion 13S (main valve port 13a) becomes a constant width within a certain allowable range L2 in the axis L direction. In this way, within the allowable range L2 of slight fluctuation in the axis L direction of the main valve body 3, the opening area between the main valve body 3 and the main valve seat 13 is parallel to the axis L so as to be constant. A columnar straight portion 13S is provided on the main valve seat 13, and in this straight portion 13S, the ridge 31a of the main valve body 3 inserted into the main valve port 13a is the main valve within the allowable range L2 in the axis L direction. It faces the portion having the maximum diameter of the port 13a.

As a result, even if the main valve body 3 floats with respect to the main valve seat 13 in the axis L direction, if the floating amount is within the allowable range L2, the protrusion 31a of the main valve body 3 and the straight portion 13S The opening area due to the gap between them becomes constant. Therefore, even when the main valve body 3 vibrates within the permissible range L2, the flow rate of the fluid flowing from the first joint pipe 11 to the second joint pipe 12 can be kept constant, and a small flow rate range can be controlled. Sex improves.

FIG. 10 is an enlarged vertical cross-sectional view of a main part of the electric valve of the fifth embodiment in the small flow rate control range state, and what is different from the first embodiment in the fifth embodiment is conduction to two places of the main valve body 3. A point where the hole 32b is formed and a point where a straight portion 13S'is provided at an end portion of the main valve seat 13. That is, as shown in FIG. 11, in the fourth embodiment, a straight portion 13S'having a diameter larger than that of the main valve port 13a is provided inside the upper end portion of the main valve seat 13, and the main valve is provided in the straight portion 13S'. A part of the main valve portion 31 of the body 3 is inserted.

In this way, within the permissible range L2 of the slight fluctuation in the axis L direction of the main valve body 3, the opening area between the main valve body 3 and the main valve seat 13 is parallel to the axis L so as to be constant. An annular straight portion 3S'is provided on the main valve seat 13. Further, the straight portion 13S'is opposed to the portion having the maximum diameter of the main valve seat 3 within the allowable range L2 in the axis L direction.

As a result, even if the main valve body 3 floats with respect to the main valve seat 13 in the axis L direction, if the floating amount is within the allowable range L2, the straight portion 13S'and the main valve body 3 are between each other. The opening area due to the gap becomes constant. Therefore, even when the main valve body 3 vibrates, the flow rate of the fluid flowing from the first joint pipe 11 to the second joint pipe 12 can be kept constant, and the controllability in the small flow rate region is improved.

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 the above embodiment 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. It is provided and, together with the compressor 95, the four-way valve 96, the outdoor heat exchanger 94 and the electronic expansion valve 93, constitutes a heat pump type refrigeration cycle. 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 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 the home air conditioner, and may be a commercial air conditioner. It can be applied not only to air conditioners but also to various refrigerators.

Further, in the above embodiment, an example in which a taber portion as an abutting portion is formed on the needle valve side and a step portion as an abutting portion is formed on the main valve body side has been described, but a columnar step is formed on the needle valve side. A portion may be formed, and a mortar-shaped taber portion may be formed on the main valve body side so as to face the columnar step portion.

As described above, 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 not deviating 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 Guide hole 21 Press-fitting part 22 Upper guide part 23 Lower guide part 24 Holder part 24a Female thread part 25 Flange part 3 Main valve body 3S Straight part 3R Sub valve chamber 3a Step part (contact part)
31 Main valve part 32 Holding part 32a Needle guide hole 33 Sub valve seat 34 Retainer 35 Main valve spring 4 Needle valve (secondary valve body)
41 Guide boss 41a Tapered part (contact part)
42 Needle part 42a Straight part 42b Needle 43 Washer 5 Drive part 5A Stepping motor 5B Thread feed mechanism 5C Stopper mechanism 51 Rotor shaft 51a Male thread part 52 Magnet rotor 52a Protrusion part 53 Stator coil 54 Spring receiver 55 Coil spring 4'Needle valve 41' Guide Boss part 43'Connecting rod 7a Spring receiver 7 Coil spring (contact part)
4 ″ Needle valve 41 ″ Guide boss 42 ″ Needle valve (secondary valve body)
13S Straight part 31a Rough 13S'Straight part 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 (7)

A main valve body formed on the periphery of a main valve port provided in the main valve chamber of the valve body is provided with a main valve body that is close to or separated from the main valve seat in the axial direction of the main valve port, and the main valve body is provided. It is a two-stage electric valve equipped with a sub-valve seat formed on the periphery of a sub-valve port provided in the internal sub-valve chamber and a sub-valve body that is close to or separated from the sub-valve.
The straight portion parallel to the axis so as to keep the opening area between the main valve body and the main valve seat constant within the allowable range of slight fluctuation in the axis direction of the main valve body is described. An electric valve provided on at least one of a main valve body and the main valve seat. The main valve body is provided with the columnar straight portion inserted into the main valve port, and the straight portion faces the portion having the minimum diameter of the main valve port within the allowable range in the axial direction. The electric valve according to claim 1. The main valve port of the main valve seat constitutes the cylindrical straight portion through which a part of the main valve body is inserted, and the straight portion constitutes the main valve body of the main valve body within the allowable range in the axial direction. The electric valve according to claim 1, wherein the electric valve faces a protrusion in a valve port. Any one of claims 1 to 3, wherein the sub-valve body is configured to press the main valve body against the main valve seat without contacting the sub-valve seat. The electric valve described in the section. The sub-valve body and the main valve body are provided with a contact portion, and one of the contact portions is a tapered portion whose central axis is the axis of the sub-valve port, and the other is a step whose central axis is the axis. The electric valve according to claim 4, wherein the electric valve is a part. The contact portion between the sub-valve body and the main valve body is contacted via a spring installed between a flange portion provided on the sub-valve body and a step portion provided on the main valve body. The electric valve according to claim 4, wherein the electric valve is brought into contact with the electric valve. 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 dehumidification valve.

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