CN113915339A - Two-stage electric valve and refrigeration cycle system - Google Patents

Two-stage electric valve and refrigeration cycle system Download PDF

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Publication number
CN113915339A
CN113915339A CN202110365751.3A CN202110365751A CN113915339A CN 113915339 A CN113915339 A CN 113915339A CN 202110365751 A CN202110365751 A CN 202110365751A CN 113915339 A CN113915339 A CN 113915339A
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CN
China
Prior art keywords
sub
valve
port
valve body
main
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Granted
Application number
CN202110365751.3A
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Chinese (zh)
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CN113915339B (en
Inventor
小池亮司
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Publication of CN113915339A publication Critical patent/CN113915339A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • F16K1/38—Valve members of conical shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/54—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)

Abstract

The invention provides a two-stage motor-operated valve which can obtain a noise reduction effect particularly in a small flow control area. A two-stage motor-operated valve comprising: a valve body; a main valve port formed in a main valve seat in a main valve chamber within the valve body; a main valve body supported by the valve body so as to be movable in the axial direction, the main valve body being capable of opening and closing a main valve port; and a sub valve body that is close to or apart from a sub valve seat formed at a peripheral edge of a sub valve port placed in a sub valve chamber in the main valve body, wherein a gap between the sub valve port of the main valve body and a needle portion of the sub valve body constitutes a throttle portion for passing a fluid, a diameter expansion space that is larger than the sub valve port in a radial direction of the sub valve port and a muffler member that passes the fluid on a downstream side of the diameter expansion space are provided on a downstream side of the sub valve port, and a length L1 of the sub valve port in an axial direction and a length L3 of the diameter expansion space from an outlet of the sub valve port to the muffler member in the axial direction satisfy a relationship of L1 > L3.

Description

Two-stage electric valve and refrigeration cycle system
Technical Field
The invention relates to a two-stage electric valve and a refrigeration cycle system.
Background
Conventionally, as a two-stage motor-operated valve provided in a refrigeration cycle system such as an air conditioner, there are known: the present invention relates to a valve device including a main valve element and a sub valve element, wherein a small flow rate control for passing a fluid such as a refrigerant is performed at a throttle portion formed in a gap between a sub port of the main valve element and the sub valve element, and a noise reduction member is provided downstream of the sub valve element in order to suppress a fluid passing noise when passing through the throttle portion, and a noise reduction effect is obtained particularly in a small flow rate control region (for example, see patent document 1).
Documents of the prior art
Patent document
Patent document 1: chinese patent application publication No. 06870750 specification
Disclosure of Invention
Problems to be solved by the invention
However, in the conventional two-stage motor-operated valve disclosed in patent document 1, there are concerns that: since the muffler member is provided directly below the throttle portion, the fluid whose pressure is reduced when passing through the throttle portion and bubbles are generated therein collides with the muffler member in a state where the flow velocity is high, the velocity is rapidly reduced, the pressure is rapidly recovered, a large number of bubbles are broken before the subdivision, large sound is generated, and the suppression of the fluid passing sound to a desired degree cannot be achieved.
The invention aims to provide a two-stage electric valve and a refrigeration cycle system which can obtain a silencing effect especially in a small flow control area.
Means for solving the problems
The two-stage motor-operated valve of the present invention comprises: a valve body; a main valve port formed in a main valve seat in a main valve chamber within the valve body; a main valve body supported by the valve body so as to be freely movable in an axial direction, the main valve body being capable of opening and closing the main valve port; and a sub valve body that is close to or distant from a sub valve seat formed at a peripheral edge of a sub valve port provided in a sub valve chamber in the main valve body, wherein a gap between the sub valve port of the main valve body and a needle portion of the sub valve body constitutes a throttle portion through which a fluid passes, a diameter expansion space that is larger in diameter than the sub valve port in a radial direction of the sub valve port and a noise suppressing member that passes the fluid on a downstream side of the diameter expansion space are provided on a downstream side of the sub valve port, and a length L1 of the sub valve port in the axial direction and a length L3 of the diameter expansion space from an outlet of the sub valve port to the noise suppressing member in the axial direction satisfy a relationship of L1 > L3.
According to the present invention, since the flow velocity of the fluid passing through the throttle portion is reduced in the expanded diameter space and then the fluid flows into the silencer member, the bubbles can be subdivided by the silencer member before the pressure is restored to burst a large number of bubbles inside. In particular, in a small flow rate control region, a noise reduction effect can be achieved, and the sound of passing fluid can be suppressed.
At this time, it is preferable that the length L1 of the sub-port in the axial direction and the length L4 of the sound deadening member in the axial direction satisfy a relationship of L1 < L4.
Further, it is preferable that the needle portion of the sub-valve body has a flow rate control portion inserted into the sub-port and gradually decreasing in diameter toward an outlet side of the sub-port, and a length L1 of the sub-port in the axial direction and a length L2 of the needle portion in the axial direction satisfy a relationship of L1 < L2.
The refrigeration cycle system of the present invention is characterized by including the electrically operated valve.
According to the present invention, as in the motor-operated valve described above, a silencing effect can be obtained particularly in a small flow rate control region, and since the fluid passage sound can be suppressed, a silent refrigeration cycle can be realized.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the motor-operated valve and the refrigeration cycle system of the present invention, a noise reduction effect can be obtained particularly in a small flow rate control region.
Drawings
Fig. 1 is a longitudinal sectional view showing a two-stage motor-operated valve according to an embodiment of the present invention.
Fig. 2 is an enlarged longitudinal sectional view of a main portion of the two-stage motor-operated valve, and is an explanatory diagram for explaining a detailed configuration.
Fig. 3 is an enlarged longitudinal sectional view of a main portion of the two-stage motor-operated valve, and is an explanatory view for explaining the operational effect.
Fig. 4 is a diagram showing an example of the refrigeration cycle system of the present invention.
In the figure:
10-two-stage electric valve, 1-valve body, 1C-main valve chamber, 13-main valve seat, 14-main valve port, L-axis, 2-main valve core, 23-auxiliary valve chamber, 2C-auxiliary valve seat, 24-auxiliary valve port, 3-auxiliary valve core, 32-needle part, 33-throttling part, 5-expanding space, 6-silencing part, 32 a-flow control part, 90-freezing circulation system.
Detailed Description
A two-stage motor-operated valve according to an embodiment of the present invention will be described with reference to fig. 1. The motor-operated valve 10 of the present embodiment is a two-stage motor-operated valve, and includes: a valve main body 1; a main valve port 14 formed in the valve main body 1; a main valve element 2 capable of opening and closing the main valve port 14; an auxiliary valve port 24 in main valve element 2; a sub-valve body 3 that is close to or away from a sub-valve seat 2C formed on the peripheral edge of the sub-valve port 24; and a stepping motor 4 as a driving section. The concept of "top and bottom" in the following description corresponds to the top and bottom in the drawing of fig. 1.
The valve main body 1 includes a cylindrical valve housing member 1A and a support member 1B fixed to an upper end opening portion of the valve housing member 1A. The valve housing member 1A has a cylindrical main valve chamber 1C formed therein, and the valve housing member 1A is provided with a primary joint pipe 11 communicating with the main valve chamber 1C from the side surface side and allowing a fluid such as a refrigerant to flow therein, and a secondary joint pipe 12 communicating with the main valve chamber 1C from the bottom surface side and allowing a fluid to flow out. The support member 1B is a resin molded product, and is fixed to the valve housing member 1A by welding via a metal fixing portion 15.
The main valve port 14 is formed in a circular cross-sectional shape in the valve housing member 1A from a main valve seat 13 provided at a position where the main valve chamber 1C communicates with the secondary joint pipe 12 toward the secondary joint pipe 12 side.
The main valve element 2 is a part for opening and closing the main valve port 14, and includes a valve element main portion 2A of the main valve portion 21 that seats on and unseats from the main valve seat 13, a stopper portion 2B, and a sub-valve seat 2C. The spool 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 a fluid flows; and a sub-valve port 24 penetrating the sub-valve seat 2C in the direction of the axis L. The cylindrical portion 22 has a plurality of communication holes 25 formed in its circumferential surface, and an insertion hole 26 formed in its inner circumferential surface along the axis L direction. The sub-valve chamber 23 communicates with the main valve chamber 1C through a communication hole 25. The stopper 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 stopper portion to regulate a rising position of the sub-valve body 3 provided at a lower end of the rotor shaft 46. The sub valve seat 2C is provided on the secondary joint pipe 12 side of the sub valve chamber 23. The valve body main portion 2A is formed with a stepped shape from the upper end portion thereof to the lower side, and a main valve spring 27 is disposed between the stepped shape and the top surface of the support member 1B. The main valve 2 is biased toward the main valve seat 13 (closing direction) by the main valve spring 27.
The sub port 24 is formed in a circular cross section from the sub valve seat 2C toward the secondary joint pipe 12 side in the main valve body 2. Further, inside the cylindrical portion 22, on the downstream side of the sub-valve port 24, there are provided: a cylindrical diameter-expanding space 5 having a diameter larger in the radial direction than the sub-valve port 24; and a cylindrical muffler member 6 for passing the fluid on the downstream side of the expanded diameter space 5. Here, the muffler member 6 is formed in a disc shape from a porous material, a metal mesh, or the like. An annular holding portion 21c is fitted into a stepped portion 21a formed at the lower end of the main valve portion 21, and holds the outer periphery of the lower end of the muffler component 6.
The sub valve body 3 is a portion that changes the opening degree of the sub valve port 24 formed in the main valve body 2. The sub-valve body 3 includes: a cylindrical sub-valve base 3A; an auxiliary valve portion 3B projecting downward from the auxiliary valve base portion 3A; an axial gasket 3C provided on the upper side of the sub-valve base 3A; and an auxiliary valve spring (not shown) provided inside the auxiliary valve base 3A. 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 sub-valve portion 3B has a rod portion 31 and a needle portion 32 at the lower end of the rod portion 31. The needle portion 32 constitutes a throttle portion 33 that passes fluid through a gap with the sub-valve port 24. As shown in fig. 2, the needle portion 32 has a flow rate control portion 32a that is inserted into the sub-port 24 and gradually decreases in diameter toward the outlet side of the sub-port 24. The axial washer 3C can abut against the upper surface of the sub-valve base 3A and the lower surface of the stopper portion 2B, and the frictional force between the abutting surfaces is extremely small. Further, an insertion hole is provided in an upper portion of the sub valve base portion 3A to insert the rotor shaft 46, and a sub valve spring is disposed between a flange portion (not shown) formed at a lower end portion of the rotor shaft 46 and an upper end portion of the sub valve portion 3B joined to a bottom portion of the sub valve base portion 3A. The sub valve body 3 is biased in the sub valve seat 2C direction (approaching direction) with respect to the rotor shaft 46 (magnetic rotor 44) by the sub valve spring. The sub valve base 3A may be formed integrally with the rotor shaft 46 and the sub valve portion 3B, 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 stepping motor 4 is a portion that moves the sub-valve body 3 back and forth in the direction of the axis L and also moves the main valve body 2 back and forth in the direction of the axis L via the sub-valve body 3. The stepping motor 4 includes: a screw feed mechanism 42 for advancing and retracting the sub-valve body 3 by rotation of the magnetic rotor 44; and a stopper mechanism 43 that restricts rotation of the magnetic rotor 44. The stepping motor 4 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 in the direction of the axis L, and has an upper end inserted into a guide 47 of the stopper mechanism 43. The screw feeding mechanism 42 is configured by integrally forming a male screw portion 46B in an intermediate portion of the rotor shaft 46, and screwing the male screw portion 46B to the female screw portion 17 of the support member 1B. When the magnetic rotor 44 rotates, the male screw portion 46b of the rotor shaft 46 is guided by the female screw portion 17, whereby the magnetic rotor 44 and the rotor shaft 46 move backward in the direction of the axis L, and the sub-valve body 3 also moves up or down along the axis L.
The stopper mechanism 43 includes: a cylindrical guide 47 hanging from the top inside the housing 18; a helical 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 so as to be rotatable and vertically movable. The movable slider 49 is provided with a claw portion 49a protruding radially outward, and the magnetic rotor 44 is provided with an extension portion 44a extending upward and coming into contact with the claw portion 49 a. When the magnetic rotor 44 rotates, the extension portion 44a presses the claw portion 49a, and thereby the movable slider 49 rotates along the guide line body 48 and moves up and down. The guide wire body 48 is formed with 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. By bringing the movable slider 49 into contact with the upper end stopper 48a and the lower end stopper 48b, the rotation of the movable slider 49 is stopped, whereby the rotation of the magnetic rotor 44 is restricted, and the ascending or descending of the sub-valve body 3 is also stopped.
In the present embodiment, as shown in fig. 2, a length L1 of the sub-valve port 24 in the direction of the axis L and a length L3 of the enlarged diameter space 5 from the outlet of the sub-valve port 24 to the upper surface of the muffler member 6 in the direction of the axis L satisfy the relationship of L1 > L3. Further, the length L1 of the sub-valve port 24 in the direction of the axis L and the length L4 of the muffler member 6 in the direction of the axis L satisfy the relationship L1 < L4. Further, the length L1 of the sub-valve port 24 in the direction of the axis L and the length L2 of the flow rate control portion 32a of the needle portion 32 in the direction of the axis L satisfy the relationship L1 < L2. Here, the length L2 of the flow rate control portion 32a of the needle portion 32 in the direction of the axis L is a distance from the upper end surface of the sub-valve seat 13 to the lower end of the needle portion 32 of the sub-valve body 3 at a position (the lowermost end of the sub-valve body 3) when the sub-valve body 3 descends to be closest to the sub-valve seat 2C in a state where the main valve body 2 is seated on the main valve seat 13 and the main valve port 14 is closed.
The two-stage motor-operated valve 10 configured as described above operates as follows. First, the main valve portion 21 of the main valve 2 of the two-stage motor-operated valve 10 is seated on the main valve seat 13, and the main valve port 14 is in a closed valve state in which it is closed. In the two-stage motor-operated valve 10, when the sub-valve body 3 is located closest to the sub-valve port 24, the sub-valve body 3 is not seated on the sub-valve seat 2C, but a flow path is formed by a gap between the outer peripheral surface of the needle portion 32 of the sub-valve body 3 and the inner peripheral surface of the sub-valve port 24. Therefore, the fluid flowing into the primary valve chamber 1C from the primary joint pipe 11 flows into the secondary valve chamber 23 through the communication hole 25 of the spool main portion 2A. The fluid that has flowed into the sub valve chamber 23 flows downward of the main valve portion 21 through a gap between the outer peripheral surface of the needle portion 32 of the sub valve body 3 and the sub valve port 24, and flows out from the main valve port 14 to the secondary joint pipe 12. That is, even if the valve opening degree (valve lift) is zero (the sub valve portion 3B is at the lowermost position), a minute flow rate is generated.
Next, the stepping motor 4 is driven to rotate the magnetic rotor 44 to raise the sub-valve body 3, whereby the needle portion 32 of the sub-valve portion 3B of the sub-valve body 3 is raised inside the sub-valve port 24, the flow path of the gap between the needle portion 32 of 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 in a state where the main valve body 2 is closed is the small flow rate control region. When the sub-valve body 3 is further raised, the axial washer 3C abuts against the stopper 2B, the main valve body 2 is pulled up by the sub-valve body 3, and the main valve portion 21 is unseated from the main valve seat 13. The control region in which the opening degree of the main valve port 14 is changed by moving the main valve element 2 away from the seat is a large flow rate control region in which the flow rate is largely changed and the flow rate is maximized in the fully opened state in which the main valve element 2 is farthest from the main valve port 14.
According to the present embodiment described above, as shown in fig. 3, the length L1 of the sub-valve port 24 in the direction of the axis L and the length L3 of the expanded diameter space 5 from the outlet of the sub-valve port 24 to the upper surface of the muffler member 6 in the direction of the axis L satisfy the relationship of L1 > L3, and the flow velocity of the fluid passing through the throttle portion 33 is reduced in the expanded diameter space 5 and then the fluid flows into the muffler member 6, so that the bubbles can be subdivided by the muffler member 6 before the pressure is restored and a large number of bubbles inside are broken. In particular, a noise reduction effect can be obtained in a small flow rate control region, and the sound of passing fluid can be suppressed.
In the present embodiment, the length L1 of the sub-valve port 24 in the direction of the axis L and the length L4 of the muffler member 6 in the direction of the axis L satisfy the relationship L1 < L4. With this configuration, the ability of the muffler member 6 to subdivide the bubbles in the fluid is higher than the increase in the flow velocity of the fluid in the throttle portion 33, and therefore the sound of the fluid passing through can be further suppressed.
In the present embodiment, the length L1 of the sub-valve port 24 in the direction of the axis L and the length L2 of the flow rate control portion 32a of the needle portion 32 in the direction of the axis L satisfy the relationship L1 < L2. With this configuration, the shorter the length of the throttle portion 33 is than the length of the flow rate control portion 32a of the needle portion 32, the more the increase in the flow velocity of the fluid can be suppressed, and therefore the fluid passage noise can be further suppressed.
Next, a refrigeration cycle system of the present invention will be described with reference to fig. 4. Fig. 4 is a diagram showing an example of the refrigeration cycle system of the present invention.
The refrigeration cycle 90 shown in fig. 4 is used for an air conditioner such as a household air conditioner, for example. The two-stage motor-operated valve 10 of the above embodiment is provided between the first indoor-side heat exchanger 91 (operating as a dehumidifying cooler) and the second indoor-side heat exchanger 92 (operating as a dehumidifying heater) of the air conditioner. The two-stage motor-operated valve 10 constitutes a heat pump refrigeration cycle together with a compressor 95, a four-way valve 96, an outdoor heat exchanger 94, and an electronic expansion valve 93. The first indoor-side heat exchanger 91, the second indoor-side heat exchanger 92, and the two-stage motor-operated valve 10 are installed indoors, and the compressor 95, the four-way valve 96, the outdoor-side heat exchanger 94, and the electronic expansion valve 93 are installed outdoors, thereby constituting a cooling/heating apparatus.
The two-stage motor-operated valve 10 as a dehumidification valve is configured to fully open the main valve port 14 by the main valve 2 at the time of cooling or heating other than the dehumidification time, and to use the first indoor heat exchanger 91 and the second indoor heat exchanger 92 as one indoor heat exchanger. The integrated indoor-side heat exchanger and outdoor-side heat exchanger 94 alternatively function as an "evaporator" and a "condenser". That is, the electronic expansion valve 93 is provided between the evaporator and the condenser.
According to the refrigeration cycle 90, since the two-stage motor-operated valve 10 according to the above-described one embodiment is provided in the path of the fluid, a noise reduction effect can be obtained particularly in a small flow rate control region, and the fluid passage noise can be suppressed, so that the refrigeration cycle can be made silent.
While the embodiments for carrying out the present invention have been described in detail based on one embodiment with reference to the drawings, the specific configuration is not limited to the one embodiment, and design changes to the extent of not departing from the gist of the present invention are also included in the present invention.
For example, in the above-described example of the present invention, the two-stage motor-operated valve 10 is used for a normal air conditioner, but the present invention is not limited thereto, and may be used for a multi-air conditioner for a building, a refrigerator, and the like.

Claims (4)

1. A two-stage motor-operated valve is provided with: a valve body; a main valve port formed in a main valve seat in a main valve chamber within the valve body; a main valve body that is supported by the valve main body so as to be movable in an axial direction and that can open and close the main valve port; and a sub valve body that is close to or away from a sub valve seat formed at a periphery of a sub valve port provided in a sub valve chamber in the main valve body,
the two-stage electrically operated valve is characterized in that,
a restriction portion for passing a fluid is formed by a gap between the sub-port of the main valve body and the needle portion of the sub-valve body,
a diameter-expanding space that is larger in diameter than the sub-valve port in a radial direction of the sub-valve port, and a sound-deadening member that passes a fluid on a downstream side of the diameter-expanding space, are provided on a downstream side of the sub-valve port,
a length L1 of the sub-port in the axial direction and a length L3 of the enlarged diameter space from the outlet of the sub-port to the muffler component in the axial direction satisfy a relationship of L1 > L3.
2. Two-stage electrically operated valve according to claim 1,
the length L1 of the sub-valve port in the axial direction and the length L4 of the sound deadening member in the axial direction satisfy the relationship of L1 < L4.
3. Two-stage electrically operated valve according to claim 1 or 2,
the needle portion of the sub-valve element has a flow rate control portion that is inserted into the sub-valve port and gradually decreases in diameter toward an outlet side of the sub-valve port,
a length L1 of the sub-valve port in the axis direction and a length L2 of the flow control portion of the needle portion in the axis direction satisfy a relationship of L1 < L2.
4. A refrigeration cycle system is characterized in that,
a two-stage electrically operated valve as claimed in any one of claims 1 to 3.
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