阅读说明：本技术 电动阀以及冷冻循环系统 (Electric valve and refrigeration cycle system ) 是由 北见雄希 小池亮司 于 2020-03-17 设计创作，主要内容包括：本发明提供一种电动阀以及冷冻循环系统,其在小流量控制区域和大流量控制区域内控制流量,在大流量控制区域内将主阀芯(3)的全开位置作为预定位置来使全开流量稳定,并且防止主阀弹簧(3a)的过度压缩,从而防止由老化变化等引起的主阀弹簧(3a)的变形。具备开闭主阀口(13a)的主阀芯(3)、变更主阀芯(3)的副阀室(3R)的副阀口(33a)的开度的针阀(4)、向主阀口(13a)侧对主阀芯(3)进行施力的主阀弹簧(3a)、以及驱动针阀(4)沿轴线(L)方向进退的驱动部(5)。设置抵接部(231、311),在使主阀口(13a)全开的大流量控制区域内,抵接部以使主阀弹簧(3a)成为中间压缩状态的方式限制主阀芯(3)的在轴线(L)方向上的全开位置。(The invention provides an electric valve and a refrigeration cycle system, which control flow in a small flow control area and a large flow control area, stabilize the full-open flow by taking the full-open position of a main valve core (3) as a preset position in the large flow control area, and prevent the over-compression of a main valve spring (3a), thereby preventing the deformation of the main valve spring (3a) caused by aging change. The valve device is provided with a main valve body (3) for opening and closing a main valve port (13a), a needle valve (4) for changing the opening degree of a sub-valve port (33a) of a sub-valve chamber (3R) of the main valve body (3), a main valve spring (3a) for biasing the main valve body (3) toward the main valve port (13a), and a driving part (5) for driving the needle valve (4) to advance and retreat in the direction of an axis (L). Contact parts (231, 311) are provided, and in a large flow control region where the main valve port (13a) is fully opened, the contact parts limit the fully opened position of the main valve core (3) in the direction of the axis (L) in a manner that the main valve spring (3a) is in an intermediate compression state.)

1. An electrically operated valve comprising:

a main valve element for opening and closing a main valve port of the main valve chamber; an auxiliary valve body that changes an opening degree of an auxiliary valve port provided in an auxiliary valve chamber of the main valve body; a main valve spring that biases the main valve element toward the main valve port; and a driving part for driving the auxiliary valve core to advance and retreat along the axial direction,

the electric valve has two-stage flow control regions of a small flow control region in which the opening degree of the sub-valve port is changed by the sub-valve element in a state where the main valve element closes the main valve port, and a large flow control region in which the main valve element fully opens the main valve port and a large flow of fluid flows from the main valve port,

the above-mentioned electric valve is characterized in that,

and a stopper mechanism that limits a full open position of the main valve element in the axial direction so that the main valve spring is in an intermediate compressed state in the large flow control region.

2. Electrically operated valve according to claim 1,

when the sub valve body opens the sub valve port further than the small flow rate control region, the sub valve body engages with the main valve body, and the main valve body is brought into the fully open state.

3. Electrically operated valve according to claim 1 or 2,

a guide member inserted through the main valve element in the guide hole and guiding the main valve element in the axial direction,

the stopper mechanism includes a contact portion formed on the guide member and a contact portion formed on the main valve element, and the two contact portions are brought into contact with each other in the axial direction to regulate a fully open position of the main valve element in the axial direction.

4. Electrically operated valve according to claim 3,

the abutting portion on the main spool side is formed on the outer periphery of the main valve portion of the main spool, and the abutting portion on the guide member side is formed on the end portion of the guide member.

5. Electrically operated valve according to claim 3,

the stopper mechanism includes a contact portion of the guide member formed at a bottom of the guide hole and a contact portion of the main valve element formed at an end portion of the main valve element facing the bottom of the guide hole.

6. Electrically operated valve according to claim 1 or 2,

the stopper mechanism includes a contact portion of the main valve element formed around the sub-port and a contact portion of the sub-valve element formed on a columnar portion of the sub-valve element on a side of a needle portion that opens and closes the sub-port, and the main valve element is regulated in a fully open position in the axial direction by the contact of the two contact portions in the axial direction.

7. A refrigeration cycle system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve arranged between the indoor heat exchanger and the outdoor heat exchanger, and a dehumidification valve arranged on the indoor heat exchanger,

the above-described refrigeration cycle system is characterized in that,

use of an electrically operated valve as claimed in any one of claims 1 to 6 as the above-mentioned dehumidification valve.

Technical Field

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

Background

In the past, as an electric valve provided in a refrigeration cycle of an air conditioner, there is an electric valve that controls a flow rate in a small flow rate control area and a large flow rate control area. Such an electrically operated valve is used in an indoor unit (e.g., a dehumidification valve), and is disclosed in, for example, japanese patent application laid-open No. 2012 and 117584 (patent document 1).

Disclosure of Invention

Problems to be solved by the invention

In the conventional electric flow control valve (electric valve) of patent document 1, a main valve body is disposed to face a large-diameter port on a secondary joint pipe side, and the main valve body is biased toward the large-diameter port by a biasing force of a main valve spring provided between the main valve body and a support member. The opening degree of a small-diameter port provided in the main valve body is controlled by the pilot valve body so as to be a small flow rate control region. Then, the main valve body is raised together with the pilot valve body by driving of the stepping motor, so that the large-diameter port is opened, and a large flow control region is formed. The electric flow control valve is used in an indoor unit as a dehumidification valve of a refrigeration cycle, and is configured to be a large flow control region as described above, for example, during a heating operation, and to allow a large flow of fluid (refrigerant) to flow from a large-diameter port side.

However, in such a state of the large flow rate control region during the heating operation, the pressure of the fluid flowing from the large-diameter port raises the main valve element, but the full opening flow rate during the heating operation is varied and unstable due to a deviation in the full opening position of the main valve element caused by a magnitude of the pressure (pressure difference) of the fluid against the main valve spring load or a deviation in the full opening position of the main valve element caused by a deviation in the contact length when the main valve spring is compressed to the contact length. Further, since the main valve spring may be compressed to an excessive contact length in this way, the main valve spring may be deformed due to aging or the like, and the spring characteristics may be deteriorated, making it difficult to perform appropriate flow rate control.

The invention provides an electrically operated valve for controlling flow rate in a small flow rate control region and a large flow rate control region, wherein the fully open flow rate is stabilized by setting the fully open position of a main valve body as a predetermined position in the large flow rate control region, and excessive compression of a main valve spring is prevented, thereby preventing deformation of the main valve spring due to aging and the like.

Means for solving the problems

The motor-operated valve of the present invention comprises: a main valve element for opening and closing a main valve port of the main valve chamber; an auxiliary valve body that changes an opening degree of an auxiliary valve port provided in an auxiliary valve chamber of the main valve body; a main valve spring that biases the main valve element toward the main valve port; and a driving unit that drives the sub-valve element to move back and forth in an axial direction, wherein the electric valve has a two-stage flow control region including a small flow control region in which the sub-valve element changes an opening degree of the sub-valve port in a state where the main valve element closes the main valve port, and a large flow control region in which the main valve element fully opens the main valve port and a large flow of fluid flows from the main valve port, and wherein the electric valve is characterized by including a stopper mechanism that restricts a fully open position of the main valve element in the axial direction so that the main valve spring is in an intermediate compressed state in the large flow control region.

According to the present invention, the stopper mechanism positions the full open position of the main valve element so that the main valve spring is in the "intermediate compressed state". Therefore, the full open position of the main spool is positioned at a predetermined position, and the full open flow rate of the fluid is stabilized. Further, since the main valve spring is compressed only to the intermediate compression state, deformation (decrease in spring force) of the main valve spring due to aging or the like can be prevented.

In the motor-driven valve, it is preferable that the main valve element is brought into the fully open state by engaging the sub valve element with the main valve element when the sub valve element brings the sub valve port into a state of being opened further than the small flow rate control region. Therefore, it is preferable to use an electrically operated valve in which the main valve element is fully opened by the operation of a drive unit that drives the sub valve element.

Preferably, the valve device further includes a guide member that guides the main valve element in the axial direction by inserting the main valve element into the guide hole, and the stopper mechanism includes a contact portion formed on the guide member and a contact portion formed on the main valve element, and the two contact portions contact each other in the axial direction to regulate a fully open position of the main valve element in the axial direction.

In this case, the electric valve is preferably configured such that the abutment portion on the main valve spool side is formed on the outer periphery of the main valve portion of the main valve spool, and the abutment portion on the guide member side is formed on an end portion of the guide member.

In the motor-operated valve, it is preferable that the stopper mechanism includes a contact portion of the guide member formed at a bottom of the guide hole and a contact portion of the main valve element formed at an end portion facing the bottom of the guide hole.

In the electrically operated valve, it is preferable that the stopper mechanism includes a contact portion of the main valve element formed around the sub-port and a contact portion of the sub-valve element formed in a columnar portion of the sub-valve element on a needle-like portion side for opening and closing the sub-port, and the two contact portions abut against each other in the axial direction to regulate a fully open position of the main valve element in the axial direction.

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 a dehumidification valve provided in the indoor heat exchanger, and is characterized in that the electric valve described in any one of the above is used as the dehumidification valve.

According to such a refrigeration cycle system, during heating operation, control for stabilizing the full open flow rate can be performed in the same manner as the effect of the above-described motor-operated valve, and deformation (decrease in spring force) of the main valve spring can be prevented, so that a stable system can be configured.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the electric valve and the refrigeration cycle system of the present invention, in the electric valve having the two-stage flow rate control region, the full open flow rate of the fluid can be stabilized, and deformation (decrease in the elastic force) of the main valve spring can be prevented.

Drawings

Fig. 1 is a longitudinal sectional view showing a state of a small flow rate control region of an electric valve according to a first embodiment of the present invention.

Fig. 2 is a longitudinal sectional view of the main valve element of the motor-operated valve of the first embodiment in a fully open state during stop of operation or during cooling operation.

Fig. 3 is a vertical cross-sectional view of the main valve body of the motor-operated valve of the first embodiment during the heating operation in the fully open state.

Fig. 4 is a vertical cross-sectional view when fluid flows in a fully open state of an electrically operated valve according to a second embodiment of the present invention.

Fig. 5 is a vertical cross-sectional view when fluid flows in a fully open state of an electrically operated valve according to a third embodiment of the present invention.

Fig. 6 is a vertical cross-sectional view when fluid flows in a fully open state of an electrically operated valve according to a fourth embodiment of the present invention.

Fig. 7 is a diagram showing a refrigeration cycle system according to an embodiment of the present invention.

In the figure:

1-a valve housing, 1R-a main valve chamber, 11-a first joint pipe, 12-a second joint pipe, 13-a main valve seat, 13 a-a main valve port, 14-a housing, L-an axis, 2-a guide member, 2A-a guide hole, 21-a press-in portion, 22-an upper guide portion, 23-a lower guide portion, 231-an abutting portion, 24-a holder portion, 24 a-an internal thread portion, 25-a flange portion, 3-a main valve spool, 3 a-a main valve spring, 3R-a sub valve chamber, 31-a main valve portion, 311-an abutting portion, 32-a holding portion, 32A-a needle valve guide hole, 32B-a through hole, 33-a sub valve seat, 33a sub valve port, 34-a retainer, 4-a needle valve (sub valve spool), 41-a cylindrical portion, 42-a needle portion, 43-a washer, 44-a guide boss portion, 5-a drive portion, 5A-a step motor, 5B-a screw feed mechanism, 5C-a limit mechanism, 51-rotor shaft, 51 a-male screw portion, 52-magnetic rotor, 52A-protrusion, 53-stator coil, 23 ' -lower guide portion, 2A ' -guide hole, 231 ' -contact portion, 321-contact portion, 331-contact portion, 411-contact portion, 22 b-annular portion, 221-contact portion, 341-contact portion, 91-first indoor side heat exchanger, 92-second indoor side heat exchanger, 93-electronic expansion valve, 94-outdoor side heat exchanger, 95-compressor, 96-four-way valve, 100-electric valve.

Detailed Description

Next, embodiments of an electric valve and a refrigeration cycle system according to the present invention will be described with reference to the drawings. Fig. 1 is a vertical cross-sectional view of a small flow rate control region state of an electric valve of a first embodiment, fig. 2 is a vertical cross-sectional view of the electric valve of the first embodiment at the time of operation stop or cooling operation in a fully open state of a main valve body, and fig. 3 is a vertical cross-sectional view of the electric valve of the first embodiment at the time of heating operation in a fully open state of the main valve body. Note that the concept of "up and down" in the following description corresponds to the up and down in the drawings of fig. 1 to 3. The motor-operated valve 100 includes a valve housing 1, a guide member 2, a main valve body 3, a needle valve 4 as a "sub valve body", and a drive unit 5.

The valve housing 1 is formed into a substantially cylindrical shape, for example, from brass, stainless steel, or the like, and has a main valve chamber 1R inside thereof. A first joint pipe 11 that communicates with the main valve chamber 1R is connected to one side of the outer periphery of the valve housing 1, and a second joint pipe 12 is connected to a cylindrical portion that extends downward from the lower end. A cylindrical main valve seat 13 is formed on the valve housing 1 on the main valve chamber 1R side of the second joint pipe 12, the inner side of the main valve seat 13 becomes a main valve port 13a, and the second joint pipe 12 is communicated with the main valve chamber 1R through the main valve port 13 a. 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 an opening portion at the upper end of the valve housing 1. The guide member 2 includes a press-fitting portion 21 press-fitted into the inner peripheral surface of the valve housing 1, substantially columnar guide portions 22 and 23 having a smaller diameter than the press-fitting portion 21 and positioned above and below the press-fitting portion 21, a bracket portion 24 extending above the guide portion 22 disposed on the upper side, and an annular flange portion 25 provided on the outer periphery of the press-fitting portion 21. The press-fitting portion 21, the guide portions 22 and 23, and the holder portion 24 are formed as an integral resin product. The flange portion 25 is a metal plate such as brass or stainless steel, for example, and the flange portion 25 is integrated 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. 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 a female screw portion 24a coaxial with the guide hole 2A and a screw hole thereof are formed in the center of the holder portion 24. Further, the main valve element 3 is disposed inside the lower guide portion 23 and inside the guide hole 2A.

The main valve body 3 includes a main valve portion 31 that seats on and unseats from the main valve seat 13, a cylindrical holding portion 32 having a needle guide hole 32a, a sub valve seat 33 that forms the bottom of the needle guide hole 32a, and a stopper 34 provided at an end of the holding portion 32. Further, a portion of the lower side of the needle guide hole 32a becomes the sub-valve chamber 3R. A washer 43 attached to a rotor shaft 51 described below and a guide boss 44 formed integrally with the rotor shaft 51 are inserted into the needle valve guide hole 32a of the holding portion 32, and the annular stopper 34 is fixed to the upper end of the holding portion 32 by fitting or welding.

A main valve spring 3a is disposed between the stopper 34 and the upper end of the guide hole 2A, and the main valve spring 3a biases the main valve body 3 in the direction of the main valve seat 13 (closing direction). A cylindrical sub-valve port 33a centered on the axis L is formed in the center of the sub-valve seat 33. A communication hole 32b for communicating the sub-valve chamber 3R with the main valve chamber 1R is formed at least at one position on the side surface of the holding portion 32, and when the needle valve 4 serving as a sub-valve body opens the sub-port 33a, the main valve chamber 1R, the sub-valve chamber 3R, the sub-port 33a, and the main valve port 13a communicate with each other.

The needle valve 4 is integrally provided with a truncated cone-shaped needle portion 42 at a lower end portion of a rotor shaft 51 described below, and the needle portion 42 is integrally formed with the rotor shaft 51 and gradually decreases in diameter toward a tip end continuous with the rotor shaft 51. The needle valve 4 includes an annular washer 43 made of a lubricating resin and attached to the rotor shaft 51, and a guide boss 44 formed integrally with the rotor shaft 51. The washer 43 and the guide boss 44 are slidably inserted into the needle valve guide hole 32 a.

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

The stepping motor 5A includes a rotor shaft 51, a magnetic rotor 52 rotatably disposed inside the housing 14, a stator coil 53 disposed on the outer periphery of the housing 14 so as to face the magnetic rotor 52, and other yokes, exterior members, and the like, which are not shown. The rotor shaft 51 is attached to the center of the magnetic rotor 52 via a sleeve, 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 screw portion 51a is screwed into the female screw 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 constitute a screw feeding mechanism 5B.

With the above configuration, when the stepping motor 5A is driven, the magnetic rotor 52 and the rotor shaft 51 rotate, and the rotor shaft 51 moves in the direction of the axis L together with the magnetic rotor 52 by the screw feeding mechanism 5B of the male screw portion 51a of the rotor shaft 51 and the female screw portion 24a of the guide member 2. Then, the needle valve 4 moves forward and backward in the direction of the axis L, and the needle valve 4 approaches or separates from the sub-valve port 33 a. When the needle 4 is raised, the washer 43 engages with the stopper 34 of the main valve 3, and the main valve 3 moves together with the needle 4 and is unseated from the main valve seat 13. The magnetic rotor 52 is provided with a projection 52a, and the projection 52a operates the rotation restricting mechanism 5C in accordance with the rotation of the magnetic rotor 52 to restrict the lowermost end position and the uppermost end position of the rotor shaft 51 (and the magnetic rotor 52).

In the small flow rate control area state of fig. 1, the main valve port 13a is closed in a state where the main valve body 3 is seated on the main valve seat 13, and the opening degree of the sub-valve port 33a is controlled by the needle valve 4, thereby controlling the small flow rate. For example, when the needle valve 4 and the main valve element 3 are lifted in a state where the compressor of the refrigeration cycle is stopped and the fluid (refrigerant) is stopped, the main valve port 13a is fully opened as shown in fig. 2. In this way, during heating operation, a large flow of fluid (refrigerant) flows from the second joint pipe 12 to the first joint pipe 11.

Here, the lower end of the lower guide portion 23 of the guide member 2 is an abutment portion 231 constituting an annular flat surface. Further, the outer diameter of the main valve portion 31 is larger than the outer diameter of the holding portion 32, and thus an abutment portion 311 constituting an annular flat surface is formed on the outer periphery of the main valve portion 31 on the side of the holding portion 32. The contact portion 231 of the guide portion 23 and the contact portion 311 of the main valve portion 31 are disposed to face each other in the direction of the axis L. When a large flow of fluid flows out from the second joint pipe 12 as a heating operation in the state of fig. 2, the pressure (differential pressure) of the fluid acts on the main valve element 3, and the main valve element 3 rises against the biasing force of the main valve spring 3a, resulting in the state of fig. 3. At this time, in a state where the main valve spring 3a is not fully compressed, the abutment portion 311 on the outer periphery on the holding portion 32 side of the main valve portion 31 abuts against the abutment portion 231 of the lower guide portion 23 of the guide member 2, and the full open position, which is the position of the main valve body 3 in the direction of the axis L, is positioned.

As described above, the state in which the main valve spring 3a is not fully compressed to the close contact length is referred to as an "intermediate compression state". In this embodiment, the contact portion 311 and the contact portion 231 constitute a "stopper mechanism" that positions the full open position of the main valve body 3 so that the main valve spring 3a is in the "intermediate compressed state". Therefore, the full open position of main spool 3 is stabilized at a predetermined position, so that the flow rate (full open flow rate) of the fluid flowing from second joint pipe 12 to first joint pipe 11 is stabilized. Further, since the main valve spring 3a is compressed only to the intermediate compression state, it is possible to prevent deformation (decrease in spring force) of the main valve spring 3a due to aging or the like.

Fig. 4 to 6 are longitudinal sectional views of main portions when fluid flows in a fully opened state of the motor-operated valve according to the second to fourth embodiments. The second to fourth embodiments are different from the first embodiment in the stopper mechanism, and the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 1 to 3, and overlapping descriptions are omitted as appropriate.

In the second embodiment of fig. 4, in the guide member 2, the inner diameter of the guide hole 2A 'of the lower guide portion 23' is made larger than the inner diameter of the guide hole 2A of the upper guide portion 22, and thus an abutment portion 231 'constituting an annular flat surface is formed between the guide hole 2A' and the guide hole 2A. An abutment portion 321 that forms an annular flat surface is formed at the axial middle of the holding portion 32 of the main valve portion 31. The contact portion 231' of the guide member 2 is disposed opposite to the contact portion 321 on the main valve element 3 side in the direction of the axis L.

The contact portion 321 and the contact portion 231' constitute a "stopper mechanism" that positions the full open position of the main valve element 3 so that the main valve spring 3a is in the "intermediate compressed state", as in the first embodiment. Thereby, the full open position of main valve element 3 is stabilized, and the flow rate (full open flow rate) of the fluid flowing from second joint pipe 12 to first joint pipe 11 is stabilized. Further, deformation (decrease in spring force) of the main valve spring 3a can be prevented.

In the third embodiment of fig. 5, there is a columnar portion 41 which is connected from the guide boss portion 44 to the needle portion 42 side, has a diameter smaller than the outer diameter of the guide boss portion 44 and larger than the inner diameter of the sub-valve port 33a, and a contact portion 411 which forms an annular flat surface is formed at an end portion of the columnar portion 41 on the needle portion 42 side. Thus, the contact portion 411 is disposed so as to face the contact portion 331 around the sub valve port 33a of the sub valve seat 33 in the axis L direction.

The contact portion 411 and the contact portion 331 constitute a "stopper mechanism" that positions the full open position of the main valve element 3 so that the main valve spring 3a is in the "intermediate compressed state" as in the first embodiment. Thereby, the full open position of main valve element 3 is stabilized, and the flow rate (full open flow rate) of the fluid flowing from second joint pipe 12 to first joint pipe 11 is stabilized. Further, deformation (decrease in spring force) of the main valve spring 3a can be prevented.

In the fourth embodiment of fig. 6, the stopper 34 is raised in height in the axial direction, and an abutting portion 341 forming an annular flat surface is formed at the upper end of the stopper 34. An annular portion 22b protruding toward the stopper 34 is formed on the ceiling portion of the guide hole 2A of the guide member 2, and the lower end of the annular portion 22b forms an abutment portion 221 forming an annular flat surface. In the "intermediate compressed state" of the main valve spring 3a, the contact portion 341 of the stopper 34 contacts the contact portion 221 of the annular portion 22 b.

The contact portion 341 and the contact portion 221 constitute a "stopper mechanism" that positions the full open position of the main valve element 3 so that the main valve spring 3a is in the "intermediate compressed state" as in the first embodiment. Thereby, the full open position of main valve element 3 is stabilized, and the flow rate (full open flow rate) of the fluid flowing from second joint pipe 12 to first joint pipe 11 is stabilized. Further, deformation (decrease in spring force) of the main valve spring 3a can be prevented.

Next, a refrigeration cycle system of the present invention will be described with reference to fig. 7. The refrigeration cycle is used for, for example, an air conditioner such as a household air conditioner. The motor-operated valve 100 of each of the embodiments described above is provided between the first indoor-side heat exchanger 91 (which operates as a cooler during dehumidification) and the second indoor-side heat exchanger 92 (which operates as a heater during dehumidification) of the air conditioner, and constitutes a heat pump refrigeration cycle together with the compressor 95, the four-way valve 96, the outdoor-side heat exchanger 94, and the electronic expansion valve 93. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the motor-operated 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, thereby constituting a cooling/heating apparatus.

In the motor-operated valve 100 according to the embodiment of the dehumidification valve, the main valve is fully opened during cooling or heating other than dehumidification, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 serve as one indoor heat exchanger. The integrated indoor and outdoor heat exchangers 94 alternatively function as "evaporators" or "condensers". That is, the electric valve 93 as an electronic expansion valve is provided between the evaporator and the condenser.

The present invention is not limited to the above-described embodiments, and includes other configurations and the like that can achieve the object of the present invention, and the present invention also includes modifications and the like described below. For example, although the above embodiment shows an example of the motor-operated valve 100 used for an air conditioner such as a home air conditioner, the motor-operated valve of the present invention is not limited to the home air conditioner, and may be applied to a commercial air conditioner, an air conditioner, and various refrigerators.