CN111828659B

CN111828659B - Valve device and refrigeration cycle system

Info

Publication number: CN111828659B
Application number: CN202010254950.2A
Authority: CN
Inventors: 小池亮司; 北见雄希; 中川大树
Original assignee: Saginomiya Seisakusho Inc
Current assignee: Saginomiya Seisakusho Inc
Priority date: 2019-04-23
Filing date: 2020-04-02
Publication date: 2022-05-17
Anticipated expiration: 2040-04-02
Also published as: CN111828659A

Abstract

The invention provides a valve device and a refrigeration cycle system capable of suppressing clogging and reducing noise. The fluid having passed through the sub-valve port (24) passes through the retention space (29) and the communication flow path section (28) in this order and then flows into the joint pipe. In this path, since there are no fine holes of the metal mesh, clogging can be suppressed. Further, by retaining the fluid in the retention space 29, the flow velocity can be reduced, and the noise can be reduced.

Description

Valve device and refrigeration cycle system

Technical Field

The present invention relates to a valve device and a refrigeration cycle system.

Background

Conventionally, there has been proposed a two-stage electric expansion valve including a piston-shaped main valve element for opening and closing a main valve port, and a stem-shaped sub valve element for opening and closing a sub valve port provided in the main valve port (see, for example, patent document 1). In the motor-driven expansion valve described in patent document 1, a rotation-linear movement conversion means is provided to convert the rotation of the rotor into a movement in the valve lifting direction. In addition, by this movement in the valve lift direction, the sub valve body moves first and the sub valve port opens to perform flow rate control of a small flow rate, and the main valve body also moves due to the movement of the sub valve body and the main valve port opens to perform flow rate control of a large flow rate.

Documents of the prior art

Patent document

Patent document 1: japanese laid-open patent publication No. 2000-266194

Disclosure of Invention

Problems to be solved by the invention

In the conventional motor-operated expansion valve described in patent document 1, depending on conditions such as a pressure difference between the inlet port and the outlet port and an opening degree of the sub-port, a flow velocity of a fluid passing through the sub-port becomes high, which may cause noise. Therefore, a structure is considered in which noise is reduced by covering the sound generation unit with a sound deadening member. As such a sound deadening member, a member having a plurality of through holes formed, such as a metal mesh, is considered, but there is a possibility that clogging may occur due to dust or the like in the fluid.

The invention aims to provide a valve device and a refrigeration cycle system capable of inhibiting blockage and reducing noise.

Means for solving the problems

A valve device according to the present invention includes a main valve body for opening and closing a main valve port, and a sub valve body for moving in a moving direction of approaching to or separating from a sub valve port formed in the main valve body, the main valve body including: a bottomed cylindrical wall covering the sub-valve port when viewed from the main-valve-port side; a communication flow path portion for communicating the inner and outer spaces of the bottomed cylindrical wall; and a retention space formed inside the bottomed cylindrical wall at a position that is farther from the secondary port than the opening of the communication flow passage section in the moving direction, the retention space being configured such that the fluid that has passed through the secondary port is once retained in the retention space, and then passes through the communication flow passage section and flows into the primary port.

According to the valve device of the present invention, the fluid that has passed through the sub-port passes through the retention space and the communication flow path portion in this order and then flows into the main port. In this path, the fine pores of the metal mesh are not present, and therefore clogging can be suppressed. Furthermore, the fluid is retained in the retention space, so that the flow velocity can be reduced and the noise can be reduced. Thus, according to the valve device of the present invention, clogging can be suppressed while reducing noise.

Further, it is preferable that at least a part of the opening of the communication flow path portion is formed at a position closer to the sub valve port than a tip end of the sub valve body on the retention space side when the sub valve body moves to a position farthest from the sub valve port in the moving direction.

According to this configuration, the fluid that has stagnated in the stagnation space and flows to the opening of the communication flow path portion can be favorably guided to the opening of the communication flow path portion by the tip of the sub-valve body.

Further, it is also preferable that the opening of the communication flow path portion is formed at a position farther from the sub port than a tip end of the sub valve body on the retention space side when the sub valve body moves to a position closest to the sub port in the moving direction.

According to such a configuration, it is possible to suppress collision of the fluid flowing into the inner space of the bottomed cylindrical wall through the gap between the sub-valve body and the sub-valve port and the fluid flowing from the retention space to the communication flow path portion at the position on the tip end side of the sub-valve body. Therefore, vibration of the sub-valve body due to such a flow of fluid is less likely to occur, and vibration noise and the like can be suppressed.

Further, it is preferable that the sub-valve port is a circular opening, and an inner diameter of the bottomed cylindrical wall is equal to or smaller than an inner diameter of the sub-valve port.

According to such a configuration, during manufacturing, for example, the space formation from the sub-valve port to the inner space of the bottomed cylindrical wall can be temporarily performed by drilling with a drill having a diameter corresponding to the inner diameter of the sub-valve port.

The communication flow path portion may be a lateral hole that penetrates the peripheral wall of the bottomed cylindrical wall so as to be orthogonal to the peripheral wall, or may be an inclined hole that penetrates the peripheral wall of the bottomed cylindrical wall so as to be inclined with respect to the peripheral wall.

With this configuration, the communicating flow path portion can be easily formed by drilling or the like with the drill into the cylindrical wall with a bottom.

Preferably, the main valve element includes a main valve portion that is formed in a flange shape, extends beyond an outer peripheral surface of the bottomed cylindrical wall, and seats on or unseats a main valve seat in which the main valve port is formed.

According to this configuration, since the bottomed cylindrical wall can be disposed away from the inner edge of the main valve opening, the opening size of the main valve opening can be ensured.

Further, it is preferable that a sound deadening member is disposed on a bottom side of the bottomed cylindrical wall in the retention space.

With this configuration, the fluid flowing into the retention space once hits the muffler member and then flows into the communication flow path portion. This makes it possible to subdivide bubbles in the fluid, which is one factor of the fluid flow sound of the communicating flow path portion, and further reduce noise. Further, since the muffler member is disposed on the bottom side of the bottomed cylindrical wall in the retention space, even if the muffler member is clogged with foreign matter, the passage from the sub-valve port to the communication passage portion is not clogged. Thus, according to the above configuration, noise can be further reduced without causing clogging of the flow path.

The refrigeration cycle system of the present invention includes a compressor, a condenser, an expansion valve, and an evaporator, and is characterized in that any one of the valve devices is used as the expansion valve.

According to such a refrigeration cycle, it is possible to reduce noise while suppressing clogging of the valve device as described above, and to suppress transmission of vibration generated by the valve device (expansion valve) to a device on the downstream side.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the valve device and the refrigeration cycle system of the present invention, the fluid from the sub-port is allowed to flow through the communication flow path section and flow to the main valve port after being accumulated, and thus clogging can be suppressed and noise can be reduced.

Drawings

Fig. 1 is a longitudinal sectional view showing an electric valve according to a first embodiment of the present invention.

Fig. 2 is a longitudinal sectional view showing a main part of the electric valve in an enlarged manner.

Fig. 3 is a longitudinal sectional view showing an enlarged view of a main portion of the motor-operated valve when the valve opening degree is maximized.

Fig. 4 is a schematic configuration diagram showing a refrigeration cycle system of the present invention.

Fig. 5 is an enlarged longitudinal sectional view of a main portion of an electric valve according to a second embodiment of the present invention.

Fig. 6 is a longitudinal sectional view showing an enlarged view of a main portion of the motor-operated valve when the valve opening degree is maximized.

Fig. 7 is an enlarged longitudinal sectional view of a main portion of an electric valve according to a third embodiment of the present invention.

Fig. 8 is a longitudinal sectional view showing an enlarged view of a main portion of the motor-operated valve when the valve opening degree is maximized.

Description of the symbols

10. 10B, 10C-electric valve (valve device), 14-main valve port, 2-main valve core, 21-main valve part, 24-sub valve port, 28, 30-communicating flow path part, 29-retention space, 2D, 2E-bottom cylindrical member, 3, 6-sub valve core, 3B, 6B-sub valve part, 13-main valve seat, 14-main valve port, 90-refrigeration cycle system, 91-first indoor side heat exchanger (evaporator), 92-second indoor side heat exchanger (condenser), 93-compressor, 95-outdoor side heat exchanger.

Detailed Description

Embodiments of the present invention will be described below with reference to the drawings. In the second embodiment, the same components and components having the same functions as those described in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and description thereof is omitted.

[ first embodiment ]

An electrically operated valve as a valve device according to a first embodiment of the present invention will be described with reference to fig. 1 to 3. As shown in fig. 1, the motor-operated valve 10 of the present embodiment includes a valve housing 1, a main valve element 2, a sub-valve element 3, and a drive unit 4. Note that the concept of "top and bottom" in the following description corresponds to the top and bottom in the drawing of fig. 1.

The valve housing 1 includes a tubular valve body 1A and a support member 1B fixed inside the valve body 1A. The valve main body 1A has a cylindrical main valve chamber 1C formed therein, and the valve main body 1A is provided with a primary joint pipe 11 which communicates with the main valve chamber 1C from the side surface side and into which a refrigerant as a fluid flows, and a secondary joint pipe 12 which communicates with the main valve chamber 1C from the bottom surface side and out of which a refrigerant as a fluid flows. Further, a main valve seat 13 is formed in the valve main body 1A at a position where the main valve chamber 1C communicates with the secondary joint pipe 12, and a main valve port 14 having a circular cross-sectional shape is formed from the main valve seat 13 toward the secondary joint pipe 12 side. The support member 1B is fixed to the valve body 1A by welding using a metal fixing portion 15. The support member 1B is a resin molded product, and is formed to have a cylindrical main valve guide 16 provided on the main valve seat 13 side and a female screw portion 17 provided on the driving portion 4 side and having a female screw formed on an inner peripheral surface. A housing 18 is hermetically fixed to an upper end portion of the valve main body 1A by welding or the like.

As shown in fig. 2 and 3, the main valve element 2 includes a valve element main portion 2A having a main valve portion 21 that seats on or unseats from the main valve seat 13, a spring seat portion 2B, a sub valve seat 2C, and a bottomed cylindrical wall 2D. The valve body main portion 2A has a cylindrical portion 22 having an axial direction of the axis L, an auxiliary valve chamber 23 formed inside the cylindrical portion 22 and through which fluid flows, and an auxiliary valve port 24 penetrating the auxiliary valve seat 2C along the axis L. A plurality of communication holes 25 are formed in the circumferential surface of the cylindrical portion 22, and the sub-valve chamber 23 communicates with the main valve chamber 1C through the communication holes 25. An insertion hole 26 along the axis L is formed in the inner peripheral surface of the cylindrical portion 22 of the main valve body 2A, and the sub valve base portion 3A of the sub valve body 3 is inserted into the insertion hole 26. The spring seat portion 2B is formed in an annular shape and fixed to an upper end portion of the valve body main portion 2A, and a rotor shaft 46 is inserted into the spring seat portion. A main valve spring 27 is disposed between the upper surface of the spring seat portion 2B and the top surface of the support member 1B, and the main valve 2 is biased in the direction of the main valve seat 13 (closing direction) by the main valve spring 27.

The sub-valve body 3 is constituted by: a cylindrical sub-valve base 3A; a sub valve portion 3B configured to partially enter the sub valve port 24; a thrust washer 3C provided on the upper side of the sub-valve base 3A; and a shaft portion 3D projecting downward from the sub-valve base portion 3A along the axis L and having a sub-valve portion 3B formed at a lower end portion thereof. The sub valve base 3A is inserted into the insertion hole 26 of the main valve 2, and is supported to be movable in the vertical direction along the axis L and rotatable about the axis L. The thrust washer 3C can abut on the upper surface of the sub-valve base portion 3A and the lower surface of the spring seat portion 2B, and the frictional force between the abutting surfaces thereof becomes extremely small. An insertion hole is provided in the upper portion of the sub valve base 3A to allow the rotor shaft 46 to be inserted therethrough, and a sub valve spring is disposed between a flange portion (not shown) formed at the lower end portion of the rotor shaft 46 and the upper end portion of the shaft portion 3D joined to the bottom portion of the sub valve base 3A. The sub-valve spring biases the sub-valve body 3 in the sub-valve seat 2C direction (closing direction) with respect to the rotor shaft 46 (magnetic rotor 44). In addition, the sub valve base 3A may be formed integrally with the rotor shaft 46 and the shaft portion 3D, and in this case, the sub valve base 3A may be formed in a solid shape and the sub valve spring may be omitted.

The drive unit 4 includes: a stepping motor 41 as an electric motor; a screw feed mechanism 42 for advancing and retracting the sub-valve body 3 by rotation of the stepping motor 41; and a stopper mechanism 43 for restricting the rotation of the stepping motor 41. The stepping motor 41 includes: a magnetic rotor 44 magnetized in a multi-pole manner at its outer periphery; a stator coil 45 disposed on the outer periphery of the housing 18; and a rotor shaft 46 fixed to the magnetic rotor 44. The rotor shaft 46 is fixed to the magnetic rotor 44 via a fixing member 46a, extends along the axis L, and has an upper end portion inserted into a guide 47 of the stopper mechanism 43. A male screw portion 46B is integrally formed at an intermediate portion of the rotor shaft 46, and the male screw portion 46B is screwed with the female screw portion 17 of the support member 1B, thereby constituting the screw feeding mechanism 42. When the magnetic rotor 44 rotates, the male screw portion 46b of the rotor shaft 46 is guided by the female screw portion 17, and the magnetic rotor 44 and the rotor shaft 46 move forward and backward in the direction of the axis L, and along with this, the sub-valve body 3 also moves up and down along the axis L.

The stopper mechanism 43 includes: a cylindrical guide 47 hanging down from the top of the housing 18; a guide wire body 48 fixed to the outer periphery of the guide 47; and a movable slider 49 which is guided by the guide wire body 48 to be rotatable and movable up and down. The movable slider 49 is provided with a claw portion 49a protruding radially outward, the magnetic rotor 44 is provided with an extended portion 44a extending upward and abutting against the claw portion 49a, and when the magnetic rotor 44 rotates, the extended portion 44a presses the claw portion 49a, and the movable slider 49 rotates along the guide wire body 48 and moves up and down. An upper end stopper 48a that defines the uppermost end position of the magnetic rotor 44 and a lower end stopper 48b that defines the lowermost end position of the magnetic rotor 44 are formed in the guide wire body 48. When the movable slider 49 is brought into contact with the upper end stopper 48a and the lower end stopper 48b, the rotation of the movable slider 49 is stopped, and thereby the rotation of the magnetic rotor 44 is restricted, and the ascending or descending of the sub-valve body 3 is also stopped.

Next, the main portion of main spool 2 will be described with reference to fig. 2 and 3. As will be described later, when the main valve port 14 is used as a low-pressure side port, the positional relationship of the respective portions will be described using the "upstream side" and the "downstream side" in the following description, with the upper side of the sub valve port 24 being the upstream side and the lower side being the downstream side in fig. 2 and 3 as reference. A bottomed cylindrical wall 2D is formed integrally with the main valve body portion 2A on the downstream side of the sub valve port 24 in the main valve body portion 2A. The bottomed cylindrical wall 2D is formed so that its outer diameter is smaller than the outer diameter of the valve body main portion 2A. The main valve portion 21 is formed in a flange shape from the valve core main portion 2A so as to protrude further than the outer peripheral surface of the bottomed cylindrical wall 2D.

The bottomed cylindrical wall 2D is a bottomed cylindrical portion that covers the sub-valve port 24 when viewed from the main valve port 14 side and is formed integrally with the valve body main portion 2A with the sub-valve port 24 side as an opening side. In the present embodiment, the sub-valve port 24 is a circular opening. The space inside the bottomed cylindrical wall 2D is a single cylindrical space formed continuously with the sub-valve port 24 in the moving direction D11 of the sub-valve portion 3B of the sub-valve body 3 such that the inner diameter other than the bottom portion thereof becomes the inner diameter of the sub-valve port 24, and the sub-valve body 3 approaches (descends) or separates (ascends) from the sub-valve port 24 along the axis L. The inner space of the bottomed cylindrical wall 2D is formed by drilling with a drill, and the bottom thereof has a mortar shape corresponding to the tip of the drill. The bottomed cylindrical wall 2D is provided with a communication flow path portion 28 that communicates between the inside and outside spaces of the bottomed cylindrical wall 2D. The communication flow path portion 28 is a lateral hole that penetrates the peripheral wall of the bottomed cylindrical wall 2D perpendicularly to the peripheral wall. As shown in fig. 3, the opening of the communication flow path portion 28 is formed at a position closer to the sub-valve port 24 than the tip 3E of the sub-valve portion 3B opposite to the shaft portion 3D when the opening is raised in the moving direction D11 along the axis L to the position farthest from the sub-valve port 24. Specifically, the communication flow path portion 28 is formed such that the tip end 3E is positioned on the bottom side of the inside of the bottomed cylindrical wall 2D with respect to the entire opening of the communication flow path portion 28 even when the sub valve portion 3B rises along the axis L and is farthest from the sub valve port 24. A plurality of communication flow path portions 28 are formed in the peripheral wall of the bottomed cylindrical wall 2D. The opening area of the one communication flow path portion 28 is smaller than the opening size of the sub valve port 24. The "opening size of the sub-port 24" refers to an opening area determined according to the inner diameter of the sub-port 24.

Further, inside the bottomed cylindrical wall 2D, a space on the bottom side which is located farther from the sub-valve port 24 than the opening of the communication flow path portion 28 in the moving direction D11 becomes a fluid retention space 29. As shown by an arrow D12 of the fluid flow in fig. 2, the retention space 29 is a space in which the fluid from the sub-port 24 is temporarily retained and then flows toward the opening of the communication flow path portion 28. When the fluid flows in from the sub-valve port 24, the fluid flows temporarily in front of the opening of the communication flow path portion 28 by inertia after the fluid flows in, and flows to the retention space 29. The fluid is retained in the retention space 29, changes its direction, and flows to the opening of the communication passage section 28. A part of a tip end 3E of the sub valve portion 3B on the retention space 29 side in the sub valve body 3 is a tapered portion 3F, and the tapered portion 3F is formed in a tapered shape such that the outer diameter thereof becomes smaller toward the tip end 3E side. Here, the shaft portion 3D of the sub-valve body 3 is a cylindrical portion having a diameter larger than that of the sub-valve port 24, and the sub-valve portion 3B includes: a root tapered portion 3H tapered from the lower end of the shaft portion 3D to a position slightly smaller in diameter than the sub-valve port 24; and a short cylindrical portion 3G formed at the lower end of the root tapered portion 3H, the tapered portion 3F being formed in a shape that is further tapered from the lower end of the short cylindrical portion 3G.

The above-described motor-operated valve 10 operates as follows. First, in the state shown in fig. 1 and 2, the main valve portion 21 of the main valve 2 is seated on the main valve seat 13, and the main valve port 14 is closed. On the other hand, the sub-valve body 3 located closest to the sub-valve port 24 is not seated on the sub-valve seat 2C, and a flow path is formed by a gap between the outer peripheral surface of the sub-valve portion 3B of the sub-valve body 3 and the inner peripheral surface of the sub-valve port 24. Therefore, when the refrigerant (fluid) flows into the main valve chamber 1C from the primary joint pipe 11, the refrigerant flows into the sub valve chamber 23 through the communication hole 25 of the valve body main portion 2A as indicated by an arrow D12 in fig. 2. The refrigerant having flowed into the sub-valve chamber 23 flows into the retention space 29 through a gap between the sub-valve portion 3B and the sub-valve port 24. The refrigerant flowing into the retention space 29 is retained therein and flows in a direction changed at the bottom, flows toward the opening of the communication flow path portion 28, and flows into the opening. Then, the fluid flows into the main valve port 14 through the communication flow path portion 28, and flows out from the main valve port 14 toward the secondary joint pipe 12. In this way, the electrically-operated valve 10 is configured to generate a slight flow rate even when the valve opening degree is zero, but may be configured to seat the sub-valve portion 3B in the sub-valve opening 24 so that the flow rate is zero when the valve opening degree is zero.

As described above, the refrigerant flowing into the retention space 29 travels in the direction of the axis L of the sub-valve body 3, and hits the bottom of the retention space 29, thereby changing the traveling direction and flowing to the opening of the communication flow path portion 28. Thus, the refrigerant stagnates in the stagnation space 29 and changes the traveling direction, and the flow velocity decreases. The refrigerant that has reached the opening of the communication flow path portion 28 and flowed into the opening passes through the communication flow path portion 28 and flows out to the outside of the retention space 29. As shown in fig. 1 and 2, when the main valve port 14 is used as a low-pressure side port in a state where the main valve port 14 is closed by the main valve 2, the refrigerant flows from the sub-valve port 24 to the main valve port 14.

Next, the stepping motor 41 of the drive unit 4 is driven to rotate the magnetic rotor 44 to raise the sub-valve body 3, and the sub-valve body 3 is separated from the sub-valve port 24, whereby the flow path formed by the gap between the sub-valve portion 3B and the sub-valve port 24 is expanded, and the flow rate is gradually increased. At this time, the main valve portion 21 of the main valve 2 remains seated on the main valve seat 13, and thus the flow rate increases slightly. In this way, the control region in which the opening degree of the sub-valve body 3 is changed while the main valve body 2 is kept closed is the small flow rate control region. Next, when the sub-valve body 3 is further raised, the thrust washer 3C abuts on the spring seat portion 2B, and the main valve body 2 is pulled up by the sub-valve body 3, whereby the main valve portion 21 is unseated from the main valve seat 13. As described above, the control region for raising the main valve element 2 from the seating position (closing position) to the valve opening position (opening position) is a large flow rate control region in which the flow rate is largely changed with respect to the opening degree of the main valve element 2 (the rotation amount of the stepping motor 41 corresponds to the valve lift amount), and the flow rate is maximized in the fully opened state of the main valve element 2 shown in fig. 3. Thus, in a state where the main valve port 14 is open, the refrigerant can pass through the main valve port 14 in both directions.

According to the present embodiment described above, the refrigerant having passed through the sub-port 24 passes through the retention space 29 and the communication flow path portion 28 in this order and then flows into the main port 14. In this path, since there are no fine holes of the metal mesh, clogging can be suppressed. Further, by retaining the refrigerant in the retention space 29, the flow velocity can be reduced, and noise can be reduced. Thus, according to the present embodiment, noise can be reduced while suppressing clogging.

The opening of the communication flow path portion 28 is formed at a position closer to the sub-port 24 than the tip 3E of the sub-valve portion 3B in the sub-valve body 3 when moving to the position farthest from the sub-port 24 in the moving direction D11. This allows the refrigerant from the retention space 29 to be satisfactorily guided to the opening of the communication flow path portion 28 by the tip end 3E of the sub-valve portion 3B.

Further, since the inner diameter of the bottomed cylindrical wall 2D is equal to or smaller than the inner diameter of the sub-valve port 24 including the bottom portion thereof, the space from the sub-valve port 24 to the inside of the bottomed cylindrical wall 2D can be easily and efficiently formed as follows in the manufacturing process. That is, such space formation can be temporarily performed by, for example, drilling with a drill having a diameter corresponding to the inner diameter of the sub valve port 24.

The inner diameter of the bottomed cylindrical wall 2D may be smaller than the inner diameter of the sub-valve port 24 including the bottom portion thereof. At this time, the sub-valve port 24 is formed by drilling from the sub-valve port 24 side by a drill having a diameter corresponding to the inner diameter of the bottomed cylindrical wall 2D, and then expanding the opening by a drill having a diameter corresponding to the inner diameter of the sub-valve port 24.

Further, since the communication flow path portion 28 is a lateral hole that penetrates the peripheral wall of the bottomed cylindrical wall 2D perpendicularly to the peripheral wall, the communication flow path portion 28 can be easily formed by drilling or the like on the bottomed cylindrical wall 2D with a drill.

The main valve element 2 further includes a main valve portion 21, and the main valve portion 21 is formed in a flange shape, extends beyond the outer peripheral surface of the bottomed cylindrical wall 2D, and is seated on or unseated from the main valve seat 13. This allows the bottomed cylindrical wall 2D to be disposed apart from the inner edge of the main valve port 14, and therefore the opening size of the main valve 2 when the valve is opened can be secured.

Further, since a portion of the sub valve portion 3B of the sub valve body 3 closer to the tip end 3E becomes the tapered portion 3F, the refrigerant flowing from the retention space 29 to the opening of the communication flow path portion 28 can be favorably guided to the opening of the communication flow path portion 28 along the outer peripheral surface of the tapered portion 3F in the sub valve portion 3B.

Next, a refrigeration cycle system of the present invention will be described with reference to fig. 4. The refrigeration cycle 90 is used for an air conditioner such as a household air conditioner. The motor-operated valve 10 of the above-described embodiment is provided between a first indoor-side heat exchanger 91 (which operates as a cooler (evaporator) during dehumidification) and a second indoor-side heat exchanger 92 (which operates as a heater (condenser) during dehumidification) of an air conditioner, and constitutes a heat pump refrigeration cycle together with a compressor 93, a four-way valve 94, an outdoor-side heat exchanger 95, and an electronic expansion valve 96. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the motor-operated valve 10 are installed indoors, and the compressor 93, the four-way valve 94, the outdoor heat exchanger 95, and the electronic expansion valve 96 are installed outdoors, thereby configuring a cooling/heating apparatus.

[ second embodiment ]

An electrically operated valve as a valve device according to a second embodiment of the present invention will be described with reference to fig. 5 and 6. The electrically operated valve 10B of the present embodiment is different from the electrically operated valve 10 of the first embodiment in the shape of the bottomed cylindrical wall 2E. In the present embodiment, as in the description of the positional relationship of the main valve element 2 in the first embodiment, the positional relationship will be described using the "upstream side" and the "downstream side" in the case where the main valve element 2 closes the main valve element 14 and the main valve element 14 is used as the low-pressure side port. The method of using the motor-operated valve 10B is the same as the method of using the motor-operated valve 10.

The bottomed cylindrical wall 2E is formed in a two-stage shape having a large diameter portion 2E1 and a small diameter portion 2E2 from the sub valve port 24 side. As in the first embodiment, the internal space is a single cylindrical space continuously formed from the sub-valve port 24 to the bottom in the moving direction D11 with the inner diameter of the sub-valve port 24.

The communication flow path portion 30 is formed as an inclined hole that penetrates the peripheral wall of the bottomed cylindrical wall 2E obliquely with respect to the peripheral wall. The communication flow path portion 30 is opened to the outside of the bottomed cylindrical wall 2E at a step portion formed by the difference in outer diameters between the large diameter portion 2E1 and the small diameter portion 2E2 of the bottomed cylindrical wall 2E. On the other hand, as shown in fig. 6, the edge on the side of the sub-valve port 24 is opened closer to the sub-valve port 24 than the tip end 3E of the sub-valve portion 3B when moved to the position farthest from the sub-valve port 24 in the moving direction D11, on the inner side of the bottomed cylindrical wall 2E. A plurality of such communication flow path portions 30 as inclined holes are formed in the bottomed cylindrical wall 2E. The opening area of the one communication flow path portion 30 is smaller than the opening size of the sub-valve port 24. The "opening size of the sub-port 24" refers to an opening area determined according to the inner diameter of the sub-port 24.

Further, a space on the bottom side, which is a position farther from the sub-valve port 24 than the opening of the communication flow path portion 30 in the moving direction D11 when viewed from the sub-valve port 24, inside the bottomed cylindrical wall 2E is a retention space 31, and a space continuous with the communication flow path portion 30. The refrigerant from the sub-valve port 24 flows into the opening of the communication flow path portion 30, which is an inclined hole, after remaining in the retention space 31, and is guided by the outer peripheral surface of the tapered portion 3F near the leading end 3E of the sub-valve portion 3B to flow.

In the electric valve 10B of the present embodiment, as in the electric valve 10 of the first embodiment, in the closed state where the main valve port 14 is closed, the refrigerant flowing from the primary joint pipe 11 into the main valve chamber 1C flows into the sub-valve chamber 23 as indicated by the flow of the arrow D12 in fig. 5. The refrigerant having flowed into the sub-valve chamber 23 flows into the retention space 31 through a gap between the sub-valve portion 3B and the sub-valve port 24. The refrigerant flowing into the retention space 31 is retained therein and changes its direction, flows into the opening of the communication flow path portion 30, passes through the communication flow path portion 30, and flows out from the main valve port 14 toward the secondary joint pipe 12.

According to the present embodiment described above, the refrigerant having passed through the sub-port 24 passes through the retention space 31 and the communication flow path portion 30 in this order, and flows into the main port 14, as in the first embodiment described above. In this path, since there are no fine holes of the metal mesh, clogging can be suppressed. Further, by retaining the refrigerant in the retention space 31, the flow velocity can be reduced, and noise can be reduced. Thus, according to the present embodiment, noise can be reduced while suppressing clogging.

The communication flow path section 30 is an inclined hole that penetrates the peripheral wall of the bottom cylindrical wall 2E in an inclined manner, but such an inclined hole can be easily formed by drilling with a drill or the like.

[ third embodiment ]

An electrically operated valve as a valve device according to a third embodiment of the present invention will be described with reference to fig. 7 and 8. In the motor-operated valve 10C of the present embodiment, first, the shape of the sub-valve body 6 is different from that in the first and second embodiments described above. In the sub-valve body 6 of the present embodiment, the tapered portion 6F on the tip end side of the sub-valve portion 6B is shorter than the shape in the first and second embodiments. On the other hand, the root tapered portion 6H and the short cylindrical portion 6G in the shaft portion 6D and the sub-valve portion 6B are the same as those in the first and second embodiments. In the present embodiment, the opening of the communication flow path portion 58 is formed at the following position in the bottomed cylindrical wall 5F by shortening the tapered portion 6F of the sub valve portion 6B. That is, the opening of the communication flow path portion 58 is formed at a position farther from the sub-port 24 than the tip on the retention space 59 side in the sub-valve body 6 when moving to the position closest to the sub-port 24 in the moving direction D11. The shape and the like of the communication flow path portion 58 of the present embodiment are the same as those of the communication flow path portion 28 of the first embodiment.

Further, a sound deadening member 57 is disposed on the bottom side of the bottomed cylindrical wall 5F in the retention space 59. The sound deadening member 57 is preferably formed of a porous body. When the refrigerant flows toward the muffler 57, the muffler 57 formed of the porous body penetrates the interior of the porous body, thereby making the bubbles in the refrigerant fine and facilitating the muffling effect. In this regard, the sound deadening member 57 is preferably formed of a porous body. Examples of the porous body include a member in which a plurality of webs are laminated, a porous sintered metal, a porous expanded metal, and a porous plastic body. The material for forming the sound deadening member is not limited to the porous body, and may be formed of an elastic body such as rubber, for example. In this case, the refrigerant flowing toward the muffler elastically hits the muffler, and thereby the energy of the refrigerant is absorbed, and the bubbles in the refrigerant are refined.

Here, as in the first and second embodiments described above, the inner diameter of the bottomed cylindrical wall 5F is the inner diameter of the sub-valve port 24. However, in the present embodiment, the bottom portion of the inner side of the bottomed cylindrical wall 5F is not formed in the mortar shape as in the first and second embodiments, but formed in a flat shape as a simple cylindrical bottom portion, so that when the below-described sound-deadening member 57 is disposed, it is difficult to form a gap between the inner surface and the sound-deadening member 57.

In the motor-operated valve 10C of the present embodiment, as in the motor-operated valve 10 of the first embodiment, a slight gap is formed between the sub-valve portion 6B and the sub-valve port 24 in the closed state where the main valve port 14 is closed. In the valve-closed state, as indicated by the flow of the arrow D32 in fig. 7, the refrigerant having flowed into the main valve chamber 1C from the primary joint pipe 11 flows into the sub valve chamber 23, passes through the above-described gap, and flows into the retention space 59. The refrigerant flowing into the retention space 59 is retained therein, changes its direction while flowing through the muffler 57, flows into the opening of the communication flow path portion 58, passes through the communication flow path portion 58, and flows out from the main valve port 14 toward the secondary joint pipe 12. Thereafter, as shown in fig. 8, the sub valve portion 6B gradually opens from the sub valve port 24 to the gap therebetween until the main valve port 14 opens. The flow of the refrigerant at this time is also the same as the flow indicated by the arrow D32 in fig. 7.

According to the present embodiment described above, as in the first and second embodiments, the refrigerant is retained in the retention space 59 and flows into the communication flow path portion 58, whereby the flow velocity can be reduced and the noise can be reduced. Further, the muffler member 57 is disposed on the bottom side of the bottomed cylindrical wall 5F in the retention space 59 without blocking the flow path of the refrigerant, and can reduce noise while suppressing clogging.

In the present embodiment, the opening of the communication flow path portion 58 is formed at a position farther from the sub-port 24 than the tip of the sub-valve body 6 in the valve-closed state shown in fig. 7. This can suppress collision of the fluid flowing into the space inside the bottomed cylindrical wall 2D through the gap between the sub valve portion 3B and the sub valve port 24 and the refrigerant flowing from the retention space 59 to the communication flow path portion 58 at the position of the sub valve portion 3B. Therefore, the vibration of the sub-valve body 6 due to the flow of the fluid is less likely to occur, and vibration noise and the like can be suppressed.

In the present embodiment, the refrigerant having flowed into the retention space 59 once hits the muffler member 57 and then flows into the communication flow path portion 58. This makes it possible to further reduce noise by making the bubbles in the refrigerant, which is a factor of the refrigerant flowing noise of the communication flow path portion 58, finer. When the sound deadening member 57 is a porous body, the refrigerant enters the sound deadening member 57, and after the bubbles are narrowed by the pores constituting the porous body, the refrigerant flows to the communicating flow path portion 58. Further, since the muffler member 57 is disposed on the bottom side of the bottomed cylindrical wall 5F in the retention space 59, even if the muffler member 57 is clogged with foreign matter, the flow path from the sub-valve port 24 to the communication flow path portion 58 is not clogged. Thus, according to the above configuration, noise can be further reduced without causing blockage of the flow path.

The present invention is not limited to the first to third embodiments described above, 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, in the first embodiment, an example of the motor-operated valve 10 used for an air conditioner such as a home air conditioner is shown, but the motor-operated valve of the present invention is not limited to the home air conditioner, and may be a commercial air conditioner, and may be applied to various refrigerators and the like without being limited to the air conditioner.

In the first to third embodiments, the plurality of communication

flow path portions

28, 31, and 58 are formed, and the opening area of one communication

flow path portion

28, 31, and 58 is smaller than the opening area of the sub-valve port 24, but only one communication flow path portion may be formed, and the opening area of one communication flow path portion may be equal to or larger than the opening area of the sub-valve port 24. In this way, the number of the communicating flow path portions can be reduced by increasing the opening area of the communicating flow path portion, and the workability in forming the communicating flow path portion in the main valve body can be improved.

In the first and second embodiments, the communication

flow path portions

28 and 30 that are open at positions closer to the sub-valve port 24 than the tip of the sub-valve portion 3B when the valve is opened are illustrated. However, the opening of the communication flow path portion may be provided at the same position as the tip of the sub-valve body when the valve is opened, or may be provided at a position distant from the sub-valve port as in the third embodiment. However, by forming the opening at a position closer to the sub-valve port 24 than the tip of the sub-valve portion 3B when the valve is opened, the refrigerant can be favorably guided to the openings of the communication

flow path portions

28 and 30 by the tip of the sub-valve portion 3B, as described above. Further, by providing the opening of the communication flow path portion 58 at a position farther from the sub valve port 24 as in the third embodiment, it is possible to suppress collision of the fluid flowing into the space inside the bottomed cylindrical wall 2D through the gap between the sub valve portion 3B and the sub valve port 24 and the refrigerant flowing from the retention space 59 to the communication flow path portion 58 at the position of the sub valve portion 3B, and as a result, it is possible to suppress vibration noise and the like of the sub valve body 6 caused by such flow of the fluid, which is also the same as described above.

In the first to third embodiments described above, examples are shown in which the inner diameter of the bottomed cylindrical wall 2D is the inner diameter of the sub-valve port 24. However, for example, the inner diameter of the bottomed cylindrical wall may be larger than the inner diameter of the sub valve port. In this case, the main valve portion is configured by fixing a bottomed cylindrical wall formed in a large diameter in this manner to the valve body main portion by brazing or the like so as to cover the sub-valve port. However, by setting the inner diameter of the bottomed cylindrical wall 2D to the inner diameter of the sub valve port 24, the inner space of the bottomed cylindrical wall 2D and the sub valve port 24 can be temporarily formed by drilling with a drill or the like, as described above.

In the first to third embodiments, the communication

flow path portions

28 and 30 are shown as examples which are orthogonal or obliquely penetrated through the peripheral wall of the bottom cylindrical wall 2D. However, the communicating flow path portion may communicate the inner space and the outer space of the bottomed cylindrical wall, and the specific flow path shape is not limited. However, the communication

flow path portions

28 and 30 penetrating the peripheral wall of the bottom cylindrical wall 2D are provided, and thus, the communication flow path portions can be easily formed by drilling or the like with a drill into the bottom cylindrical wall 2D.

In the first to third embodiments described above, an example of the main valve element 2 having the main valve portion 21 that has a flange shape and projects beyond the outer peripheral surfaces of the bottomed

cylindrical walls

2D, 2E to be seated on or unseated from the main valve seat 13 is shown. However, the specific structure of how the main spool seats or unseats with respect to the main valve seat is not limited. However, since the main valve part 21 protruding in a flange shape is provided in the main valve element 2, the bottomed

cylindrical walls

2D and 2E can be disposed apart from the inner edge of the main valve port 14, and the opening size of the main valve element 2 when opened can be secured, as described above.

In the first to third embodiments, the example of the sub-valve body 3 including the sub-valve portion 3B having the tapered shape in a portion near the distal end 3E and serving as the tapered portion 3F is shown. However, the secondary valve body may be close to or separate from the secondary valve port, and the specific shape thereof is not limited. However, by configuring the sub-valve body 3 including the sub-valve portion 3B having the tapered portion 3F, the refrigerant can be favorably guided to the openings of the communication

flow path portions

28 and 30 along the outer peripheral surface of the sub-valve portion 3B, as described above.

While the embodiments of the present invention have been described in detail with reference to the drawings, the specific configuration is not limited to the embodiments, and the present invention includes design changes and the like within a range not departing from the gist of the present invention.

Claims

1. A valve device comprises a main valve body for opening and closing a main valve port, and a sub valve body moving in a moving direction approaching or separating from a sub valve port formed in the main valve body,

the above-mentioned valve device is characterized in that,

the main valve element includes: a bottomed cylindrical wall that covers the sub-valve port when viewed from the main-valve-port side, and that has a bottom that is axially opposed to and closed by the sub-valve port; a communication flow path portion for communicating the inner and outer spaces of the bottomed cylindrical wall; and a retention space formed inside the bottomed cylindrical wall at a position farther from the sub-valve port than the opening of the communication flow passage portion in the moving direction,

the fluid that has passed through the sub-port is once accumulated in the accumulation space, and then passes through the communication flow path portion and flows into the main port.

2. The valve device according to claim 1,

at least a part of the opening of the communication flow path portion is formed at a position closer to the sub valve port than a tip of the sub valve body on the retention space side when the sub valve body moves to a position farthest from the sub valve port in the moving direction.

3. The valve device according to claim 1,

the opening of the communication flow path portion is formed at a position farther from the sub-valve port than a tip of the sub-valve body on the retention space side when the sub-valve body moves to a position closest to the sub-valve port in the moving direction.

4. A valve device according to any one of claims 1 to 3,

the auxiliary valve port is a circular opening,

the inner diameter of the bottomed cylindrical wall is equal to or smaller than the inner diameter of the sub valve port.

5. A valve device according to any one of claims 1 to 3,

the communication flow path portion is a lateral hole that penetrates the peripheral wall of the bottomed cylindrical wall so as to be orthogonal to the peripheral wall.

6. A valve device according to any one of claims 1 to 3,

the communication flow path portion is an inclined hole that penetrates through a peripheral wall of the bottomed cylindrical wall in an inclined manner with respect to the peripheral wall.

7. A valve device according to any one of claims 1 to 3,

the main valve element includes a main valve portion that is formed in a flange shape, extends beyond an outer peripheral surface of the bottomed cylindrical wall, and seats on or unseats a main valve seat in which the main valve port is formed.

8. A valve device according to any one of claims 1 to 3,

a sound deadening member is disposed on a bottom side of the bottomed cylindrical wall in the retention space.

9. A refrigeration cycle system comprises a compressor, a condenser, an expansion valve and an evaporator, and is characterized in that,

use of the valve device according to any one of claims 1 to 8 as the expansion valve.