CN113915339B - 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
CN113915339B
CN113915339B CN202110365751.3A CN202110365751A CN113915339B CN 113915339 B CN113915339 B CN 113915339B CN 202110365751 A CN202110365751 A CN 202110365751A CN 113915339 B CN113915339 B CN 113915339B
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China
Prior art keywords
valve
valve port
sub
main
auxiliary
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CN202110365751.3A
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Chinese (zh)
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CN113915339A (en
Inventor
小池亮司
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Classifications

    • 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)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

The invention provides a two-stage motor-driven valve capable of obtaining silencing effect especially in a small flow control area. A two-stage electric valve is provided with: a valve body; a main valve port formed in a main valve seat in a main valve chamber in a valve main body; a main valve body that is supported by the valve body so as to be movable in the axial direction, and that can open and close the main valve opening; and an auxiliary valve element which is close to or far from the auxiliary valve seat, wherein the auxiliary valve seat is formed at the periphery of the auxiliary valve port, the auxiliary valve port is arranged in an auxiliary valve chamber in the main valve element, a gap between the auxiliary valve port of the main valve element and a needle part of the auxiliary valve element forms a throttling part for allowing fluid to pass through, an expanding space and a silencing part are arranged at the downstream side of the auxiliary valve port, the expanding space expands the diameter of the auxiliary valve port in the radial direction, the silencing part allows fluid to pass through at the downstream side of the expanding space, and the length L1 of the auxiliary valve port along the axial direction and the length L3 of the expanding space from the outlet of the auxiliary valve port to the silencing part along the axial direction meet the relation of L1 & gtL 3.

Description

Two-stage electric valve and refrigeration cycle system
Technical Field
The present invention relates to a two-stage type 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 has been known: the valve includes a main valve body and a sub valve body, and small flow rate control for passing a fluid such as a refrigerant is performed in a throttle portion formed in a gap between the sub valve port of the main valve body and the sub valve body, and a silencing member is provided downstream of the sub valve port to suppress a fluid passing sound when passing through the throttle portion, and a silencing effect is obtained particularly in a small flow rate control region (for example, refer to patent document 1).
Prior art literature
Patent literature
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 as disclosed in patent document 1, there is a concern that: since the muffler is provided immediately below the throttle, the fluid having a pressure reduced and generated bubbles therein collides with the muffler in a state of a relatively high flow velocity when passing through the throttle, the speed is rapidly reduced, and the pressure is rapidly recovered, so that a large number of bubbles are broken before the division into pieces to generate a large breaking sound, and the suppression of the fluid passing sound to a desired extent is not 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 invention comprises: a valve body; a main valve port formed in a main valve seat in a main valve chamber in the valve main body; a main valve body supported by the valve main body so as to be movable in an axial direction, the main valve body being capable of opening and closing the main valve port; and an auxiliary valve element which is close to or far from an auxiliary valve seat formed on a peripheral edge of an auxiliary valve port provided in an auxiliary valve chamber in the main valve element, wherein a gap between the auxiliary valve port of the main valve element and a needle portion of the auxiliary valve element constitutes a throttle portion through which fluid passes, an expansion space and a silencing member are provided on a downstream side of the auxiliary valve port, the expansion space is expanded in a radial direction of the auxiliary valve port than the auxiliary valve port, the silencing member passes fluid on a downstream side of the expansion space, and a length L1 of the auxiliary valve port in the axial direction and a length L3 of the expansion space from an outlet of the auxiliary valve port to the silencing 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 diameter-expanding space and then the fluid is introduced into the muffler member, the muffler member can attenuate the bubbles before the pressure is restored to collapse a large number of bubbles inside. In particular, the noise reduction effect can be achieved in the small flow control region, and the suppression of the fluid passage sound can be achieved.
In this case, it is preferable that a length L1 of the sub-valve port in the axial direction and a length L4 of the silencing 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 that is inserted into the sub valve port and has a diameter that gradually decreases toward an outlet side of the sub valve port, and that a length L1 of the sub valve port in the axial direction and a length L2 of the flow rate control portion 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 comprising the above-described electrically operated valve.
According to the present invention, as in the case of the above-described electric valve, the noise reduction effect can be obtained particularly in the small flow rate control region, and the fluid passage noise can be suppressed, so that a silent refrigeration cycle can be realized.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the electric valve and the refrigeration cycle system of the present invention, a silencing effect can be obtained particularly in a small flow 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 showing a main part of the two-stage motor-operated valve, and is an explanatory view for explaining a detailed structure.
Fig. 3 is an enlarged longitudinal sectional view showing a main part of the two-stage motor-operated valve, and is an explanatory view for explaining the operational effects.
Fig. 4 is a diagram showing an example of the refrigeration cycle system according to 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 portion, 33-throttle portion, 5-expanding space, 6-silencing component, 32 a-flow control portion and 90-refrigerating cycle 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 electric valve 10 of the present embodiment is a two-stage electric valve, and includes: a valve body 1; a main valve port 14 formed in the valve main body 1; a main valve element 2 capable of opening and closing a main valve port 14; an auxiliary valve port 24 in the main valve core 2; a sub valve element 3 which is close to or distant from a sub valve seat 2C formed on the periphery of the sub valve port 24; and a stepping motor 4 as a driving section. The concept of "up and down" in the following description corresponds to up and down in the drawing of fig. 1.
The valve body 1 includes a tubular valve housing member 1A and a support member 1B fixed to an upper end opening 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 which communicates with the main valve chamber 1C from the side surface side to allow a fluid such as a refrigerant to flow in, and a secondary joint pipe 12 which communicates with the main valve chamber 1C from the bottom surface side to allow the fluid to flow out. The support member 1B is a resin molded product, and is welded and fixed to the valve housing member 1A by a metal fixing portion 15.
The main valve port 14 is formed in the valve housing member 1A so as to have a circular cross-section from a main valve seat 13 provided at a position where the main valve chamber 1C communicates with the secondary joint pipe 12 to the secondary joint pipe 12 side.
The main valve body 2 is a part for opening and closing the main valve port 14, and has a valve body main portion 2A, a stopper portion 2B, and a sub valve seat 2C of a main valve portion 21 that is seated on or unseated from the main valve seat 13. The valve element main portion 2A includes: a cylindrical portion 22 axially extending in the direction of the axis L; a sub-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 peripheral surface portion, and has insertion holes 26 formed in its inner peripheral 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 the upper end portion of the valve body main portion 2A, and a rotor shaft 46 is inserted therein to regulate the rising position of the sub valve body 3 provided at the 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 in a stepped shape from an upper end portion to a lower side thereof, and a main valve spring 27 is disposed between the stepped shape and a top surface of the support member 1B. The main valve element 2 is biased in the main valve seat 13 direction (closing direction) by the main valve spring 27.
The sub-valve port 24 is formed in the main spool 2 so as to have a circular cross-section from the sub-valve seat 2C toward the secondary joint pipe 12. Further, on the inner side of the cylindrical portion 22, downstream of the sub-valve port 24, there is provided: a cylindrical expansion space 5 which expands in the radial direction compared with the sub-valve port 24; and a cylindrical silencing member 6 for passing the fluid on the downstream side of the expansion space 5. Here, the muffler member 6 is formed in a circular plate shape from a porous material, a metal mesh, or the like. Further, a stepped portion 21a formed at the lower end portion of the main valve portion 21 is fitted with an annular holding portion 21c, and the outer periphery of the lower end portion of the muffler component 6 is held.
The sub valve element 3 is a part for changing the opening of the sub valve port 24 formed in the main valve element 2. The sub spool 3 includes: a cylindrical sub valve base 3A; a sub valve portion 3B protruding downward from the sub valve base portion 3A; an axial washer 3C provided on the upper side of the sub valve base 3A; and a sub valve spring (not shown) provided inside the sub valve base 3A. The sub-valve base 3A is inserted into the insertion hole 26 of the main valve element 2, and is supported so as to be movable in the vertical direction along the axis L and rotatable about the axis L. The sub valve portion 3B has a stem portion 31 and a needle portion 32 at the lower end portion of the stem portion 31. The needle portion 32 constitutes a throttle portion 33 for passing fluid through a gap between the needle portion and 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-valve port 24 and gradually decreases in diameter toward the outlet side of the sub-valve port 24. The axial gasket 3C can abut against the upper surface of the sub valve base 3A and the lower surface of the stopper portion 2B, and the friction force between the abutting surfaces thereof becomes extremely small. A rotor shaft 46 is inserted through an insertion hole provided in the upper portion of the sub valve base 3A, 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 sub valve portion 3B joined to the bottom portion of the sub valve base 3A. By this sub valve spring, the sub valve element 3 is biased in the sub valve seat 2C direction (approaching direction) with respect to the rotor shaft 46 (magnetic rotor 44). In this case, 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 stepper motor 4 is a part that advances and retreats the sub-valve body 3 in the axis L direction and advances and retreats the main valve body 2 also in the axis L direction via the sub-valve body 3. The stepping motor 4 includes: a screw feed mechanism 42 for advancing and retreating 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 whose outer peripheral portion is magnetized to a plurality of poles; 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. A male screw portion 46B is integrally formed in the 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 feed 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, whereby the magnetic rotor 44 and the rotor shaft 46 move forward and 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 spiral guide wire body 48 fixed to the outer periphery of the guide 47; and a movable slider 49 rotatably and vertically movable guided by the guide wire body 48. 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 abutting the claw portion 49 a. When the magnetic rotor 44 rotates, the extension 44a presses the claw 49a, and the movable slider 49 rotates along the guide wire body 48 and moves up and down. An upper end stopper 48a defining the uppermost position of the magnetic rotor 44 and a lower end stopper 48b defining the lowermost position of the magnetic rotor 44 are formed on the guide wire body 48. 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, and thereby the rotation of the magnetic rotor 44 is restricted, and the raising and lowering of the sub-valve body 3 are also stopped.
In the present embodiment, as shown in fig. 2, 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. The length L1 of the sub-valve port 24 in the direction of the axis L and the length L4 of the muffler 6 in the direction of the axis L satisfy the relationship of L1 < L4. 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 of L1 < L2. Here, the length L2 of the flow control portion 32a of the needle portion 32 in the axis L direction 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 seat 3 at a position (the lowermost end of the sub valve seat 3) when the sub valve seat 3 is lowered to be closest to the sub valve seat 2C in a state where the main valve seat 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 spool 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. When the sub valve body 3 is positioned closest to the sub valve port 24, the secondary 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 from the primary joint pipe 11 into the main valve chamber 1C flows into the sub valve chamber 23 through the communication hole 25 of the valve body main portion 2A. The fluid flowing into the sub valve chamber 23 flows downward of the main valve portion 21 through the 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 (valve lift) is zero (the position where the sub-valve portion 3B is the lowest end), a minute flow rate is generated.
Then, 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 enlarged, and the flow rate is gradually increased. At this time, since the main valve portion 21 of the main valve body 2 remains seated on the main valve seat 13, the increase in flow rate is small. In this way, the control region in which the opening degree of the sub valve element 3 is changed in the state where the main valve element 2 is closed is a small flow rate control region. When the sub valve body 3 is further lifted, the axial washer 3C comes into contact with the stopper portion 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 unseating the main valve element 2 in this manner is a large flow rate control region in which the flow rate is greatly changed, and the flow rate is maximized in the fully open 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 axial direction 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 axial direction L satisfy the relationship of L1 > L3, and the flow velocity of the fluid passing through the throttle portion 33 decreases in the expanded diameter space 5 and then the fluid flows into the muffler member 6, so that the muffler member 6 can divide the air bubbles into a large number of air bubbles before the pressure is recovered and the large number of air bubbles inside are broken. In particular, the noise reduction effect can be obtained in the small flow control region, and the suppression of the fluid passage sound can be realized.
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 6 in the direction of the axis L satisfy the relationship of L1 < L4. With such a configuration, the ability of the silencing member 6 to break down bubbles in the fluid is higher than the increase in the flow rate of the fluid in the throttle unit 33, and therefore, suppression of the fluid passage noise can be further achieved.
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 of L1 < L2. With such a configuration, the shorter the length of the throttle portion 33 than the length of the flow rate control portion 32a of the needle portion 32, the more the increase in the flow rate of the fluid can be suppressed, and therefore the suppression of the fluid passage sound can be further realized.
Next, a refrigeration cycle system according to the present invention will be described with reference to fig. 4. Fig. 4 is a diagram showing an example of the refrigeration cycle system according to the present invention.
The refrigeration cycle system 90 shown in fig. 4 is used in, for example, an air conditioner such as a household air conditioner. The two-stage motor-operated valve 10 of the above embodiment is provided between a first indoor side heat exchanger 91 (operating as a dehumidification cooler) and a second indoor side heat exchanger 92 (operating as a dehumidification heater) of the air conditioner. The two-stage motor 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 heat exchanger 91, the second indoor heat exchanger 92, and the two-stage motor valve 10 are installed indoors, and the compressor 95, the four-way valve 96, the outdoor heat exchanger 94, and the electronic expansion valve 93 are installed outdoors, thereby constituting a cooling/heating device.
The two-stage motor valve 10 serving as a dehumidification valve is configured such that the main valve port 14 is fully opened by the main valve body 2 during cooling or heating other than dehumidification, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 are one indoor heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 alternatively functions 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 fluid path, a noise reduction effect can be obtained particularly in a small flow rate control region, and suppression of the fluid passage noise can be achieved, so that a silent refrigeration cycle can be achieved.
The embodiment for carrying out the present invention has been described in detail based on one embodiment with reference to the drawings, but the specific configuration is not limited to this one embodiment, and design changes to the extent that they do not depart 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 to this, and may be used for a multi-air conditioner for a building, a refrigerator, or the like.

Claims (4)

1. A two-stage electric valve is provided with: a valve body; a main valve port formed in a main valve seat in a main valve chamber in the valve main body; a main valve body that is supported by the valve body so as to be movable in an axial direction, and that can open and close the main valve port; and a sub valve core which is close to or far from a sub valve seat formed at the periphery of a sub valve port provided in a sub valve chamber in the main valve core,
the two-stage motor-operated valve is characterized in that,
a throttle part for passing fluid is formed by a gap between the auxiliary valve port of the main valve core and a needle part of the auxiliary valve core,
an expansion space that expands in the radial direction of the auxiliary valve port compared with the auxiliary valve port, and a silencing member that passes fluid on the downstream side of the expansion space are provided on the downstream side of the auxiliary valve port,
the length L1 of the auxiliary valve port along the axis direction and the length L3 of the expanding space from the outlet of the auxiliary valve port to the silencing component along the axis direction satisfy the relation of L1 > L3,
the diameter of the auxiliary valve port from the inner peripheral surface of the auxiliary valve port to the inner peripheral surface of the diameter expansion space is larger than the inner diameter of the auxiliary valve port and the diameter of the needle part of the auxiliary valve core.
2. The two-stage motor-operated valve as set forth in claim 1, wherein,
the length L1 of the auxiliary valve port along the axial direction and the length L4 of the silencing component along the axial direction meet the relation of L1 < L4.
3. The two-stage motor-operated valve according to claim 1 or 2, wherein,
the needle portion of the sub valve element has a flow control portion which is inserted into the sub valve port and whose diameter gradually becomes smaller toward an outlet side of the sub valve port,
the length L1 of the auxiliary valve port along the axial direction and the length L2 of the flow control part of the needle part along the axial direction meet the relation of L1 < L2.
4. A refrigeration cycle system, characterized in that,
a two-stage motor-operated valve according to any one of claims 1 to 3.
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