JP7107881B2 - Electric valve and refrigeration cycle system - Google Patents

Description

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

Conventionally, as an electric valve provided in the refrigeration cycle of an air conditioner, there is an electric valve that controls the flow rate in a small flow rate control region and a large flow rate control region. Such a motor-operated valve has a use (for example, a dehumidification valve) mounted on an indoor unit, and is disclosed in Japanese Patent Application Laid-Open No. 2012-117584 (Patent Document 1), for example.

JP 2012-117584 A

In the conventional electric flow control valve (motorized valve) disclosed in Patent Document 1, a main valve body is arranged opposite to a large-diameter port on the secondary joint pipe side, and the main valve body is provided between the main valve body and a support member. It is biased toward the large-diameter port by the biasing force of the valve spring. A pilot valve element controls the degree of opening of a small-diameter port provided in the main valve element to provide a small flow rate control region. Further, by driving the stepping motor to raise the main valve body together with the pilot valve body, the large diameter port is opened to provide a large flow rate control region. Furthermore, this electric flow control valve is used as a dehumidifying valve in a refrigeration cycle system inside an indoor unit. ing.

However, in such a state of large flow rate control area during heating operation, the pressure of the fluid flowing from the large diameter port raises the main valve body, but the pressure (differential pressure) of the fluid opposing the main valve spring load increases. The full open position of the main valve body varies depending on the size, and when the main valve spring is compressed to the tight contact length, the full open position of the main valve body fluctuates due to variations in the tight contact length. rice field. In addition, since there is a risk that the main valve spring will be excessively compressed to the contact length in this way, the main valve spring may be deformed due to aging, etc., and the spring characteristics may deteriorate, making it difficult to properly control the flow rate. become.

The present invention is a motor operated valve that controls the flow rate in a small flow rate control range and a large flow rate control range, in which the full open position of the main valve body is set to a predetermined position in the large flow control range to stabilize the full open flow rate, and the excessive main valve spring is An object of the present invention is to prevent excessive compression and prevent deformation of a main valve spring due to aging or the like.

A motor-operated valve according to the present invention includes a main valve body for opening and closing a main valve port of a main valve chamber, a sub-valve body for changing the degree of opening of the sub-valve port of a sub-valve chamber provided in the main valve body, and the main valve body. A main valve spring that biases the valve body toward the main valve port, and a drive unit that drives the sub valve body to move forward and backward in an axial direction, the main valve body closing the main valve port. a small flow rate control region in which the sub-valve body changes the opening degree of the sub-valve port; and , wherein the main valve spring is a compression coil spring, and in the large flow rate control region, the strands of the coil of the main valve spring are all in the compression direction. a stopper mechanism that regulates the fully open position in the axial direction of the main valve body by setting the main valve spring to an intermediate compression state, which is a state in which the main valve spring is not completely compressed to the contact length , which is the axial length of the main valve spring when it is in close contact with the It is characterized by having

According to the present invention, the stopper mechanism places the main valve spring in the "intermediate compression state" and positions the main valve body at the fully open position. Therefore, since the fully open position of the main valve body is determined at a predetermined position, the fully open flow rate of the fluid is stabilized. Further, since the main valve spring is compressed only to the intermediate compression state, it is possible to prevent deformation (settling) of the main valve spring due to deterioration over time.

Further, when the sub-valve body further opens the sub-valve port beyond the small flow rate control region, the sub-valve body engages with the main valve body to fully open the main valve body. state is preferred. Accordingly, it is preferable to use an electrically operated valve in which the main valve body is fully opened by the operation of the drive section that drives the sub-valve body.

Further, a guide member for inserting the main valve body into the guide hole and guiding the main valve body in the axial direction is provided, and the stopper mechanism is formed by a contact portion formed in the guide member and the main valve body. It is preferable that the main valve body is restricted from the fully open position in the axial direction by the contacting of both the abutting portions in the axial direction.

At this time, the abutting portion on the side of the main valve body is formed on the outer periphery of the main valve portion of the main valve body, and the abutting portion on the side of the guide member is formed on the end portion of the guide member. is preferred.

Further, the stopper mechanism is composed of a contact portion formed at the bottom of the guide hole of the guide member and a contact portion formed at the end facing the bottom of the guide hole of the main valve body. Motor operated valves with

Further, the stopper mechanism includes a contact portion formed in the main valve body around the sub-valve port and a contact portion formed in a cylindrical portion on the side of the needle portion for opening and closing the sub-valve port of the sub-valve body. It is preferable that the motor-operated valve is composed of a contact portion and a contact portion that abuts in the axial direction to restrict the fully opened position of the main valve body in the axial direction.

A 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 dehumidification valve provided in an exchanger, wherein any one of the motor operated valves is used as the dehumidification valve.

According to such a refrigeration cycle system, it is possible to perform stable control of the full-open flow rate during heating operation in the same manner as the aforementioned effect of the motor-operated valve, and to prevent deformation (settling) of the main valve spring. A stable system can be constructed.

According to the motor-operated valve and the refrigeration cycle system of the present invention, in the motor-operated valve having two-stage flow control regions, the full-open flow rate of the fluid can be stabilized, and deformation (settling) of the main valve spring can be prevented.

FIG. 4 is a vertical cross-sectional view of the motor operated valve according to the first embodiment of the present invention in a small flow rate control region state; FIG. 4 is a vertical cross-sectional view of the motor-operated valve of the first embodiment when the main valve body is fully open and the operation is stopped or when the cooling operation is performed; FIG. 4 is a vertical cross-sectional view of the motor-operated valve of the first embodiment during heating operation with the main valve body fully open. FIG. 10 is a vertical cross-sectional view of the electrically operated valve of the second embodiment of the present invention when the fluid is flowing in the fully open state; FIG. 11 is a vertical cross-sectional view of the electrically operated valve of the third embodiment of the present invention when the fluid is flowing in the fully open state; FIG. 10 is a vertical cross-sectional view of the electric valve according to the fourth embodiment of the present invention when the fluid is flowing in the fully open state. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the refrigerating-cycle system of embodiment of this invention.

Next, an embodiment of an electrically operated valve and a 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 motor-operated valve of the first embodiment in a small flow rate control region state, and FIG. 2 is a longitudinal section of the motor-operated valve of the first embodiment when the main valve body is fully open and the operation is stopped or cooling operation is performed. FIG. 3 and FIG. 3 are vertical cross-sectional views of the motor-operated valve of the first embodiment during heating operation with the main valve body fully open. It should be noted that the concept of "up and down" in the following description corresponds to up and down in the drawings of FIGS. 1 to 3. FIG. This electrically 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 an actuator 5 .

The valve housing 1 is made of, for example, brass, stainless steel, or the like and has a substantially cylindrical shape, and has a main valve chamber 1R inside. 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 main valve chamber 1R side of the second joint pipe 12 of the valve housing 1, and the inner side of the main valve seat 13 serves as a main valve port 13a. The pipe 12 is connected to the main valve chamber 1R through the main valve port 13a. The main valve port 13a is a cylindrical through-hole (through-hole) centered on the axis L. As shown in FIG. 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 press-fitted into the inner peripheral surface of the valve housing 1, substantially cylindrical 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, and upper guides. It has a holder portion 24 extending from the upper portion of 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 and 23, and the holder portion 24 are configured as an integrated 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 provided integrally with the press-fitting portion 21 made of resin by insert molding.

The guide member 2 is assembled to the valve housing 1 by the press-fitting portion 21 and 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-fit portion 21 and the upper and lower guide portions 22 and 23. A female threaded portion 24a coaxial with and a threaded hole thereof are formed. The main valve body 3 is arranged inside the guide hole 2A inside the guide portion 23 on the lower side.

The main valve body 3 includes a main valve portion 31 that is seated and separated from the main valve seat 13, a holding portion 32 that has a cylindrical needle guide hole 32a, and a sub valve seat that constitutes the bottom of the needle guide hole 32a. 33 and a retainer 34 provided at the end of the holding portion 32 . A part of the lower side of the needle guide hole 32a serves as an auxiliary valve chamber 3R. A washer 43 attached to a rotor shaft 51 and a guide boss portion 44 integrally formed with the rotor shaft 51 are inserted into the needle guide hole 32a of the holding portion 32, and a ring-shaped retainer 34 is inserted. is fixed to the upper end of the holding portion 32 by fitting or welding.

A main valve spring 3a is arranged between the retainer 34 and the upper end of the guide hole 2A. energized. A cylindrical sub-valve port 33a centered on the axis L is formed at the center of the sub-valve seat 33 . At least one side surface of the holding portion 32 is formed with a communication hole 32b that connects the sub-valve chamber 3R and the main valve chamber 1R. 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 has a truncated conical needle portion 42 which is integrally formed with the rotor shaft 51 at the lower end portion of the rotor shaft 51 to be described later. Formed and prepared. The needle valve 4 also has an annular washer 43 made of lubricating resin attached to the rotor shaft 51 and a guide boss portion 44 integrally formed with the rotor shaft 51 . The washer 43 and the guide boss portion 44 are slidably inserted into the needle guide hole 32a.

A case 14 is hermetically fixed to the upper end of the valve housing 1 by welding or the like. 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 magnet rotor 52 rotatably disposed inside the case 14, a stator coil 53 opposed to the magnet rotor 52 on the outer periphery of the case 14, and other components shown in the figure. It is composed of a yoke, an exterior member, etc. The rotor shaft 51 is attached to the center of the magnet rotor 52 via a bush, and a male threaded 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, so that the guide member 2 supports the rotor shaft 51 on the axis L. As shown in FIG. The female threaded portion 24a of the guide member 2 and the male threaded portion 51a of the rotor shaft 51 constitute a screw feed mechanism 5B.

With the above configuration, when the stepping motor 5A is driven, the magnet rotor 52 and the rotor shaft 51 are rotated. At the same time, the rotor shaft 51 moves in the axis L direction. Then, the needle valve 4 advances and retreats in the direction of the axis L, and the needle valve 4 approaches or separates from the sub-valve port 33a. Also, when the needle valve 4 rises, the washer 43 engages the retainer 34 of the main valve body 3 , and the main valve body 3 moves together with the needle valve 4 to separate from the main valve seat 13 . A projection 52a is formed on the magnet rotor 52. As the magnet rotor 52 rotates, the projection 52a operates the rotation stopper mechanism 5C, and the rotor shaft 51 (and the magnet rotor 52) is positioned at the lowest end and The uppermost position is regulated.

1, the main valve body 3 is seated on the main valve seat 13, the main valve port 13a is closed, and the opening of the sub-valve port 33a is controlled by the needle valve 4. is controlled. Further, for example, when the compressor of the refrigeration cycle system is stopped and the fluid (refrigerant) is stopped, and the needle valve 4 and the main valve body 3 are raised, the main valve port 13a is fully opened as shown in FIG. Become. As a result, a large amount of fluid (refrigerant) flows from the second joint pipe 12 to the first joint pipe 11 during heating operation.

Here, the lower end portion of the guide portion 23 on the lower side of the guide member 2 serves as a contact portion 231 forming an annular flat surface. In addition, the outer diameter of the main valve portion 31 is larger than the outer diameter of the holding portion 32, so that a contact portion 311 forming an annular flat surface is formed on the outer periphery of the main valve portion 31 on the side of the holding portion 32. ing. Further, the contact portion 231 of the guide portion 23 and the contact portion 311 of the main valve portion 31 are arranged to face each other in the direction of the axis L. As shown in FIG. When a large amount of fluid flows from the second joint pipe 12 as a heating operation in the state of FIG. It rises against the urging force and enters the state shown in FIG. At this time, while the main valve spring 3a is not completely compressed, the contact portion 311 of the outer periphery of the main valve portion 31 on the holding portion 32 side contacts the contact portion 231 of the guide portion 23 on the lower side of the guide member 2. The position of the main valve body 3 in the direction of the axis L, that is, the fully open position is determined.

A state in which the main valve spring 3a is not completely compressed to the contact length as described above is called an "intermediate compression state." The contact length is the length of the main valve spring 3a when all the strands of the coil (the cross section is shown in FIGS. 1 to 6) that constitute the main valve spring 3a are in close contact with each other in the compression direction (that is, the direction of the axis L). It is the length in the direction of the axis L. In this embodiment, the abutting portion 311 and the abutting portion 231 constitute a "stopper mechanism", and this stopper mechanism places the main valve spring 3a in an "intermediate compressed state" to position the main valve body 3 at the fully open position. do. At this time, as shown in FIG. 3, when the main valve body 3 is positioned and cannot move further in the opening direction, there is a gap in the compression direction between the wires of the coil constituting the main valve spring 3a. It has become. Therefore, before the main valve body 3 is positioned by the stopper mechanism, the main valve spring 3a is completely compressed to the contact length and the main valve body 3 is not positioned by the contact of the main valve spring 3a. Therefore, since the fully open position of the main valve body 3 is stabilized at a predetermined position (that is, the position where the contact portion 311 and the contact portion 231 contact as shown in FIG. 3) , the second joint pipe 12 to the first joint pipe 12 is stabilized. The flow rate (fully open flow rate) of the fluid flowing through the tube 11 is stabilized. Further, since the main valve spring 3a is compressed only to the intermediate compression state, deformation (settling) of the main valve spring 3a due to aging or the like can be prevented.

4 to 6 are vertical cross-sectional views of main parts of the motor-operated valve of the second to fourth embodiments when the fluid is flowing in the fully open state. In the second to fourth embodiments, the difference from the first embodiment is the stopper mechanism, and elements similar to those in the first embodiment are denoted by the same reference numerals as in FIGS. .

In the second embodiment shown in FIG. 4, in the guide member 2, the diameter of the guide hole 2A' of the guide portion 23' on the lower side is made larger than that of the guide hole 2A of the guide portion 22 on the upper side. A contact portion 231' forming an annular plane is formed between the guide hole 2A and the guide hole 2A. Further, a contact portion 321 forming an annular flat surface is formed in the middle of the holding portion 32 of the main valve portion 31 in the axial direction. The abutting portion 231' of the guide member 2 and the abutting portion 321 on the main valve body 3 side are arranged to face each other in the direction of the axis L. As shown in FIG.

The abutting portion 321 and the abutting portion 231' constitute a "stopper mechanism", and this stopper mechanism places the main valve spring 3a in an "intermediately compressed state" to fully open the main valve body 3, as in the first embodiment. Locate position. As a result, the full open position of the main valve body 3 is stabilized, and the flow rate (full open flow rate) of the fluid flowing from the second joint pipe 12 to the first joint pipe 11 is stabilized. Moreover, deformation (settling) of the main valve spring 3a can be prevented.

In the third embodiment of FIG. 5, there is a cylindrical portion 41 having a diameter smaller than the outer diameter of the guide boss portion 44 connecting from the guide boss portion 44 to the needle portion 42 side and larger than the diameter of the auxiliary valve port 33a. A contact portion 411 forming an annular flat surface is formed at the end of the portion 41 on the needle portion 42 side. As a result, the contact portion 411 is arranged to face the contact portion 331 around the sub-valve port 33a of the sub-valve seat 33 in the direction of the axis L. As shown in FIG.

The abutting portion 411 and the abutting portion 331 constitute a "stopper mechanism", and this stopper mechanism puts the main valve spring 3a into an "intermediate compressed state" and the main valve body 3 is in the fully open position as in the first embodiment. position. As a result, the full open position of the main valve body 3 is stabilized, and the flow rate (full open flow rate) of the fluid flowing from the second joint pipe 12 to the first joint pipe 11 is stabilized. Moreover, deformation (settling) of the main valve spring 3a can be prevented.

In the fourth embodiment shown in FIG. 6, the height of the retainer 34 in the axial direction is increased, and the contact portion 341 forming an annular flat surface is formed at the upper end of the retainer 34 . An annular portion 22b projecting toward the retainer 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 serves as a contact portion 221 forming an annular flat surface. . Then, in the "intermediate compression state" of the main valve spring 3a, the contact portion 341 of the retainer 34 contacts the contact portion 221 of the annular portion 22b.

The abutting portion 341 and the abutting portion 221 constitute a "stopper mechanism", and this stopper mechanism puts the main valve spring 3a in an "intermediate compressed state" and the main valve body 3 is in the fully open position as in the first embodiment. position. As a result, the full open position of the main valve body 3 is stabilized, and the flow rate (full open flow rate) of the fluid flowing from the second joint pipe 12 to the first joint pipe 11 is stabilized. Moreover, deformation (settling) of the main valve spring 3a can be prevented.

Next, the refrigerating cycle system of the present invention will be described based on FIG. Refrigerating cycle systems are used, for example, in air conditioners such as domestic air conditioners. The motor-operated valve 100 of each of the above embodiments is installed between the first indoor heat exchanger 91 (operating as a cooler during dehumidification) and the second indoor heat exchanger 92 (operating as a heater during dehumidification) of the air conditioner. , and together with a compressor 95, a four-way valve 96, an outdoor heat exchanger 94 and an electronic expansion valve 93, constitutes a heat pump refrigerating cycle. 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. They make up the heating and cooling system.

In the motor-operated valve 100 of the embodiment as a dehumidification valve, the main valve body is in a fully open state during cooling or heating other than during dehumidification, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 are connected to one indoor heat exchanger. A heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 function alternatively as an "evaporator" and a "condenser". That is, the electric valve 93 as an electronic expansion valve is provided between the evaporator and the condenser.

It should be noted that the present invention is not limited to the above-described embodiments, 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-described embodiment, the motor-operated valve 100 used in an air conditioner such as a domestic air conditioner was exemplified, but the motor-operated valve of the present invention is not limited to a domestic air conditioner, and may be a commercial air conditioner. It is applicable not only to air conditioners but also to various types of refrigerators.

Although the abutment portion of the stopper mechanism in the embodiment is an annular flat surface covering the entire circumference of the axis L, it is not limited to this and may be a partial flat surface.

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. Even if there is a change in design without departing from the gist of the invention, it is included in the present invention.

1 valve housing 1R main valve chamber 11 first joint pipe 12 second joint pipe 13 main valve seat 13a main valve port 14 case L axis 2 guide member 2A guide hole 21 press fitting portion 22 upper guide portion 23 lower guide portion 231 Contact portion 24 Holder portion 24a Female screw portion 25 Flange portion 3 Main valve element 3a Main valve spring 3R Sub-valve chamber 31 Main valve portion 311 Contact portion 32 Holding portion 32a Needle guide hole 32b Conduction hole 33 Sub-valve seat 33a Sub-valve port 34 retainer 4 needle valve (sub-valve)
41 Cylindrical portion 42 Needle portion 43 Washer 44 Guide boss portion 5 Driving portion 5A Stepping motor 5B Screw feed mechanism 5C Stopper mechanism 51 Rotor shaft 51a Male screw portion 52 Magnet rotor 52a Projection portion 53 Stator coil 23' Lower guide portion 2A' guide hole 231' contact portion 321 contact portion 331 contact portion 411 contact portion 22b annular portion 221 contact portion 341 contact portion 91 first indoor heat exchanger 92 second indoor heat exchanger 93 electron expansion Valve 94 Outdoor heat exchanger 95 Compressor 96 Four-way valve 100 Electric valve

Claims (7)

a main valve body that opens and closes a main valve port of a main valve chamber; a sub-valve body that changes the degree of opening of a sub-valve port of a sub-valve chamber provided in the main valve body; a main valve spring that biases the main valve body in the lateral direction; Two stages of a small flow rate control region in which the opening degree of the auxiliary valve port is changed and a large flow rate control region in which the main valve body fully opens the main valve port and allows a large flow rate of fluid to flow from the main valve port. A motor operated valve having a flow rate control region,
The main valve spring is a compression coil spring,
Intermediate compression, which is a state in which the main valve spring is not completely compressed to the contact length , which is the length of the main valve spring in the axial direction when all the coil wires of the main valve spring are in close contact with each other in the compression direction in the large flow rate control region. and a stopper mechanism for restricting the fully opened position of the main valve body in the axial direction. When the sub-valve body further opens the sub-valve port beyond the small flow rate control region, the sub-valve body engages with the main valve body to bring the main valve body into the fully open state. The motor-operated valve according to claim 1, characterized in that: A guide member is provided for inserting the main valve body into the guide hole and guiding the main valve body in the axial direction, and the stopper mechanism is formed in the contact portion formed in the guide member and the main valve body. 3. The valve body is configured to restrict the fully opened position of the main valve body in the axial direction by abutting both of the abutting portions in the axial direction. Motorized valve as described. The contact portion on the side of the main valve body is formed on the outer periphery of the main valve portion of the main valve body, and the contact portion on the side of the guide member is formed on the end portion of the guide member. The electrically operated valve according to claim 3. The stopper mechanism is composed of a contact portion formed at the bottom of the guide hole of the guide member and a contact portion formed at the end facing the bottom of the guide hole of the main valve body. 4. The motor-operated valve according to claim 3, wherein: The stopper mechanism includes an abutment portion formed on the main valve body around the sub-valve port, and a abutment portion formed on a cylindrical portion on the side of the needle portion for opening and closing the sub-valve port of the sub-valve body. 3. The motor-operated valve according to claim 1 or 2, wherein both of said abutting portions abut in said axial direction to restrict the fully opened position of said main valve body in said axial direction. 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 7. A refrigeration cycle system, wherein the motor-operated valve according to any one of claims 1 to 6 is used as the dehumidification valve.

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